CN103080544A - Integrated energy generating damper - Google Patents
Integrated energy generating damper Download PDFInfo
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- CN103080544A CN103080544A CN2011800386552A CN201180038655A CN103080544A CN 103080544 A CN103080544 A CN 103080544A CN 2011800386552 A CN2011800386552 A CN 2011800386552A CN 201180038655 A CN201180038655 A CN 201180038655A CN 103080544 A CN103080544 A CN 103080544A
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
- F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
- F03G7/08—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for recovering energy derived from swinging, rolling, pitching or like movements, e.g. from the vibrations of a machine
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/265—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs hydraulic springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/14—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers accumulating utilisable energy, e.g. compressing air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C9/00—Oscillating-piston machines or engines
- F01C9/002—Oscillating-piston machines or engines the piston oscillating around a fixed axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/26—Reciprocating-piston liquid engines adapted for special use or combined with apparatus driven thereby
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/25—Stroke; Height; Displacement
- B60G2400/252—Stroke; Height; Displacement vertical
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Hydraulic Motors (AREA)
- Fluid-Damping Devices (AREA)
- Fluid-Pressure Circuits (AREA)
- Vehicle Body Suspensions (AREA)
- Rotary Pumps (AREA)
- Vibration Prevention Devices (AREA)
Abstract
A linear energy harvesting device that includes a housing and a piston that moves at least partially through the housing when it is compressed or extended from a rest position. When the piston moves, hydraulic fluid is pressurized and drives a hydraulic motor. The hydraulic motor drives an electric generator that produces electricity. Both the motor and generator are central to the device housing. Exemplary configurations are disclosed such as monotube, twin-tube, tri-tube and rotary based designs that each incorporates an integrated energy harvesting apparatus. By varying the electrical characteristics on an internal generator, the kinematic characteristics of the energy harvesting apparatus can be dynamically altered. In another mode, the apparatus can be used as an actuator to create linear movement. Applications include vehicle suspension systems (to act as the primary damper component), railcar bogie dampers, or industrial applications such as machinery dampers and wave energy harvesters, and electro-hydraulic actuators.
Description
Technical field
Many aspects relate to damper system and catch linear energy and the rotating energy capture systems of the energy that is associated with relative movement.
Background technique
The energy that typical damper dissipates is associated with motion.The linear damping device generally includes housing, is provided with in this housing and to stretch piston mobile in the stroke in compression stroke.In piston, be provided with the aperture.When piston moved, the motion of piston was so that viscous fluid passes the aperture, to suppress motion.
Initial damper technique has used many decades and can be divided into two main cohorts: (although produced some three cartridge type dampers, these three cartridge types dampers are used for special adaptive damper and do not have mass production for single-cylinder type damper and double barreled damper.) the single-cylinder type damper is characterised in that the gas-filled type reservoir in the hydraulic jack that has the aperture in the piston head and the main fluid chamber.The double barreled damper is characterised in that to have two concentric cylinders, and wherein, inner core is filled with hydraulic fluid, and urceolus is equipped with other compressible medium of liquids and gases or some.
Summary of the invention
Conventional damper a large amount of energy that dissipated when damping is provided is such as a large amount of warm.The inventor has recognized that the improvement to conventional damper can provide energy to reclaim and dynamic damping control ability, and the low-cost damping device technology of while and routine shares a large amount of component.
Many aspects relate to the energy producing unit of catching the energy that is associated with relative movement, and the damping to motion is provided in the self-contained equipment of compactness simultaneously, thereby are provided as the ability of the direct alternative of non-energy harvesting damper.
According to an aspect, the power generation damper comprises the piston head of the oil hydraulic motor (it can be positive displacement motor in some embodiments) with integration, and wherein, oil hydraulic motor comprises the first port and the second port.The first port is communicated with the minimum cylinder volume fluid and the second port is communicated with the stretching, extension volumetric fluid.Piston head also comprises the generator that directly is connected to oil hydraulic motor.Fluid Flow in A causes the oil hydraulic motor rotation and therefore makes generator rotation, generator generation current.According to another aspect, the power generation damper comprises housing, and this housing comprises minimum cylinder volume and stretches volume.The piston head that comprises the oil hydraulic motor of integration is arranged in the housing, and oil hydraulic motor has the first port and the second port.The first port is communicated with the minimum cylinder volume fluid, and the second port is communicated with the stretching, extension volumetric fluid.Piston head also comprises the generator that directly is connected to oil hydraulic motor, so that the rotation of oil hydraulic motor causes the rotation of generator, generator produces electricity when it rotates.In first mode, piston moves through at least a portion of jounce (compression) stroke, and this causes that fluid flows to the first port from minimum cylinder volume, thereby makes oil hydraulic motor and generator rotation, and then generation current.In the second pattern, piston moves through resilience (stretching, extension) stroke at least in part, and this makes fluid flow to the second port from stretching volume, thereby makes oil hydraulic motor and generator counterrotating, and then generation current.Fluid reservoir is communicated with minimum cylinder volume or stretching, extension volumetric fluid.According to another aspect, the power generation damper comprises inner shell, and this inner shell comprises minimum cylinder volume and stretches volume.Piston is arranged in the inner shell.In first mode, piston moves through at least a portion of jounce stroke, and removes hydraulic fluid from minimum cylinder volume.In the second pattern, piston moves through rebound stroke at least in part, to remove hydraulic fluid from stretch volume.Urceolus is concentric with the inner core that comprises minimum cylinder volume and stretching, extension volume.Urceolus comprises the low pressure volume.The low pressure volume comprises compressible medium.Be arranged in the oil hydraulic motor that piston head in the inner shell holds integration, the oil hydraulic motor of this integration comprises the first port and the second port.The first port is communicated with the minimum cylinder volume fluid and the second port is communicated with the stretching, extension volumetric fluid.Piston rod be hollow and accommodate axle, this axle makes the oil hydraulic motor on the piston head be connected with generator on the other end of piston rod.The rotation of oil hydraulic motor causes the rotation of generator.Damping is provided by generator, arrives oil hydraulic motor by the axle in the piston rod, thereby has limited the Fluid Flow in A between minimum cylinder volume and the stretching, extension volume.One or more valve limit fluid enters or flows out the low pressure volume, so that during jounce, fluid flow to the low pressure volume from minimum cylinder volume, and enters the stretching, extension volume subsequently, so that the compressible medium in the low pressure volume compresses to admit rod volume.During resilience, fluid is from the low pressure volume flow to minimum cylinder volume, so that the expansion of compressible medium is with the return piston rod volume.
According on the other hand, the power generation damper comprises basic valve at the opposite place, end of the boom end with fixing of damper.The base valve comprises oil hydraulic motor, and this oil hydraulic motor comprises the first port and the second port.Oil hydraulic motor connects with electric motor.The rotation of oil hydraulic motor causes the rotation of generator.The power generation damper also comprises two concentric cylinders with inner shell, and this inner shell comprises minimum cylinder volume and stretches volume.Piston is disposed in the inner shell.In first mode, piston moves through at least a portion of jounce stroke, and removes hydraulic fluid from minimum cylinder volume.In the second pattern, piston moves through rebound stroke at least in part, and removes hydraulic fluid from stretching volume.Urceolus is concentric with the inner core that comprises minimum cylinder volume and stretching, extension volume.Urceolus comprises the low pressure volume.The low pressure volume comprises compressible medium.The first port of oil hydraulic motor directly or by valve arrange and with stretch volumetric fluid and be communicated with, and the second port of oil hydraulic motor is directly or by the valve layout and be communicated with the low pressure volumetric fluid that comprises compressible medium.
According to another aspect, the power generation damper comprises inner shell, and this inner shell comprises minimum cylinder volume and stretches volume.Piston is disposed in the inner shell.In first mode, piston moves through at least a portion of jounce stroke, and removes hydraulic fluid from minimum cylinder volume.In the second pattern, piston moves through at least in part rebound stroke and removes hydraulic fluid from stretching volume.Second with comprise minimum cylinder volume and stretch the inner core of volume concentricity and in the outside of this inner core.Space between second and inner core comprises high pressure volume.The 3rd concentricity and in second the outside with second.Space between the 3rd and second comprises the low pressure volume.High pressure volume and low pressure volume also can be configured to respectively between the 3rd and second and between second and the inner core.The low pressure volume comprises compressible medium.The oil hydraulic motor that comprises the first port and the second port is connected.The first port is communicated with the high pressure volume fluid, and the second port is communicated with the low pressure volumetric fluid.One or more valve flow limits and/or leads, so that during jounce, minimum cylinder volume is connected to high pressure volume and stretches volume and is connected to the low pressure volume, and so that during resilience, minimum cylinder volume is connected to the low pressure volume, is connected to high pressure volume and stretch volume.Therefore, aspect this, during vibrating mode and resilience pattern, be unidirectional by oil hydraulic motor mobile and rotate.Oil hydraulic motor connects with electric motor.The rotation of oil hydraulic motor causes the rotation of generator.
According on the other hand, the power generation damper comprises inner shell, and this inner shell comprises minimum cylinder volume and stretches volume.Piston is arranged in the inner shell.In first mode, piston moves through at least a portion of jounce (compression) stroke to remove hydraulic fluid from minimum cylinder volume.In the second pattern, piston moves through resilience (stretching, extension) stroke at least in part to remove hydraulic fluid from stretching volume.Oil hydraulic motor is connected to the axle that is connected to generator, generation current when this generator rotates at its axle.The hydraulic fluid pressure motor has the first port that is connected to minimum cylinder volume and the second port that is communicated with the stretching, extension volumetric fluid.In this regard, in one embodiment, for example, as integrated piston head or hydraulic motor piston head and with the mode of execution of the generator of piston rod subtend in, the second port directly is connected to the stretching, extension volume.In another embodiment, the second port is connected by urceolus, for example, and as in basic valve configuration.Oil hydraulic motor connect with generator so that in oil hydraulic motor and the generator one rotation cause another rotation.Urceolus is concentricity with the inner core that comprises minimum cylinder volume and stretching, extension volume.Urceolus comprises the external volume that is communicated with the stretching, extension volumetric fluid.Stretch volume (passing through external volume) and minimum cylinder volume and both be communicated with valve group fluid, this valve group is operable to that fluid is communicated with---being minimum cylinder volume or stretching, extension volume---than the low pressure volume so that be attached to equally the accumulator of valve group.
According to another aspect, the power generation damper comprises housing, and this housing comprises minimum cylinder volume and stretches volume.Piston is disposed in the housing.In first mode, piston moves through at least a portion of jounce (compression) stroke to remove hydraulic fluid from minimum cylinder volume.In the second pattern, piston moves through resilience (stretching, extension) stroke at least in part to remove hydraulic fluid from stretching volume.Piston head comprises the oil hydraulic motor of integration, and this integrated oil hydraulic motor comprises the first port and the second port.This first port be communicated with the minimum cylinder volume fluid and the second port with stretch volumetric fluid and be communicated with.Piston head also comprises generator, generation current when this generator rotates at its axle.The oil hydraulic motor that piston head is installed and generator electric connects so that one rotation in oil hydraulic motor and the generator causes the rotation of another one.Piston rod is both-end, has a bar section section in each side of piston head, and each bar section section is passed respectively minimum cylinder volume and stretched volume, and leaves housing from opposite both sides.
According on the other hand, the power generation damper comprises integrated motor and the generator that is attached to rotation damper.This integrated motor generator comprises oil hydraulic motor, and this oil hydraulic motor comprises the first port and the second port.Oil hydraulic motor connects with electric motor.The rotation of oil hydraulic motor causes the rotation of generator.The power generation rotation damper also comprises the input bar that is connected to the first volume and the second volume.In first mode, input bar rotation at least a portion by stroke is to remove fluid from the first volume.In the second pattern, input bar rotation at least a portion by stroke is to remove fluid from the second volume.The first port of oil hydraulic motor be communicated with the first volumetric fluid and oil hydraulic motor in the second port be communicated with the second volumetric fluid.
According on the other hand, the power generation actuator is included in the basic valve at the opposite ends place of piston rod.The base valve comprises oil hydraulic motor, and oil hydraulic motor comprises the first port and the second port.Oil hydraulic motor connects with electric motor.The rotation of oil hydraulic motor causes the rotation of generator.The power generation actuator also comprises two concentric cylinders, and it is with the inner shell that comprises minimum cylinder volume and stretch volume.Piston is arranged in the inner shell.In first mode, piston moves through at least a portion of compression stroke, so that the hydraulic fluid in the minimum cylinder volume is pressurizeed.In the second pattern, piston moves through at least in part and stretches stroke with to stretching the hydraulic fluid supercharging in the volume.Urceolus is concentricity with the inner core that comprises minimum cylinder volume and stretching, extension volume.Urceolus comprises the low pressure volume and is connected with the stretching, extension volumetric fluid.The low pressure volume comprises compressible medium.The first port of oil hydraulic motor directly or by the valve layout is communicated with the minimum cylinder volume fluid, and the second port of oil hydraulic motor directly or by the valve layout is communicated with the low pressure volumetric fluid that comprises compressible medium.
According to another aspect, the power generation actuator is included in the basic valve at the opposite ends place of piston rod.The base valve comprises oil hydraulic motor, and this oil hydraulic motor comprises the first port and the second port.Oil hydraulic motor connects with electric motor.The base valve is connected to actuator by the rectification oil hydraulic circuit, no matter so that the direction of the stroke of actuator how, the direction of hydraulic unit rotation remains unchanged.
According to another aspect, the power generation damper of describing in aforementioned paragraphs can comprise one or more directional valve and/or fluid limiting valve, these valves provide minimum cylinder volume to be communicated with the fluid that stretches between the volume, so that fluid gets around oil hydraulic motor or limit fluid is passed through oil hydraulic motor.
According to another aspect, the power generation damper of describing in aforementioned paragraphs uses with controller, and this controller reclaims the energy that produces and the kinematics character of controlling the power generation damper.In one aspect, controller is fully powered by the power generation damper.
According to another aspect, the power generation damper of describing in aforementioned paragraphs uses with spring assembly, with the state of pushing piston bar stretching, extension.According to another aspect, the power generation damper of describing in aforementioned paragraphs uses the state that enters compression with the pushing piston bar with spring assembly.
Description of drawings
Accompanying drawing is not drawn in proportion.In the accompanying drawings, represented by identical reference character at each the identical or almost identical parts shown in the different figure.For the sake of clarity, each parts is not all to be labeled out in each accompanying drawing.In the accompanying drawings:
Fig. 1 is the mode of execution that comprises the integrated piston head (IPH) of oil hydraulic motor and generator;
Fig. 2, Fig. 2 A and Fig. 2 B show another mode of execution of the alternative integrated piston head that comprises oil hydraulic motor and generator;
Fig. 3, Fig. 3 A, Fig. 3 B and Fig. 3 C show another mode of execution of the integrated piston head of the oil hydraulic motor that comprises integration and generator;
Fig. 4 and Fig. 4 A show the mode of execution of the single-cylinder type damper that comprises IPH;
Fig. 5 is the mode of execution with integrated energy recovery double barreled damper of piston head, opposed oil hydraulic motor and generator;
Fig. 6 is the mode of execution with integrated energy recovery double barreled damper of oil hydraulic motor, electric motor/generator side valve;
Fig. 7 is that the integrated energy with oil hydraulic motor, electric motor/generator side valve base valve reclaims the mode of execution of three cartridge type dampers;
Fig. 8 is double barreled IPH mode of execution, wherein, schematically shows the accumulator that is connected to the low pressure volume;
Fig. 9 is for adopting the integrated piston head mode of execution of monotubular of axis design;
Figure 10 is that the integrated energy with exteral integration formula oil hydraulic motor reclaims the rotation mode of execution;
Figure 11 and Figure 11 A show the mode of execution that integrated energy reclaims electric liquid actuator;
Figure 12 is the mode of execution of energy harvesting actuator, and the direction of the stroke of this actuator will be as what all producing the rotation of the constant direction of motor/generator;
Figure 13 and Figure 13 A show the mode of execution of integrated oil hydraulic pump/oil hydraulic motor and electric motor/generator;
Figure 14 and Figure 14 A show have oil hydraulic motor, the integrated energy of electric motor/generator side valve and basic valve reclaims the mode of execution of three cartridge type dampers; And
Figure 15 show have oil hydraulic motor, the energy of the integration of electric motor/generator and in check hydrovalve reclaims the mode of execution of three cartridge type dampers.
Embodiment
Some aspects of native system relate to integrated energy producing unit, this integrated energy producing unit can pass through high strength but the motion produce power of relative low speed, and do not need external fluid loop, these external fluid loops usually to reduce system effectiveness, cause durability issues and increase manufacture cost.Some mode of executions utilize traditional damper configuration and parts, and wherein, improvement concentrates on the integration of energy harvesting parts and fills valves in other places on the piston head and in housing.When using " damper " with reference to this system, should be noted that the present invention is not limited to the concussion system, it also is not only energy extraction device, because it also can activated.The mode of execution of described integrated energy producing unit can comprise housing and piston, and this piston moves through compression stroke at least in part when compression.Piston can at least part of moving through stretch stroke (that is to say, piston is two-way ram) in addition when stretching.When piston moved, hydraulic fluid was pressurized and be moved to drive oil hydraulic motor.Hydraulic motor-driving generator, the generator generation current.
According to an aspect, the oil hydraulic motor of connection and generator are integrated in the piston head of conventional damper.Traditional single-cylinder type configuration can use with the air charged accumulator at the base portion place of damper.Alternately, can use with integrated piston head with the bitubular design of selective valve regulation accumulator configuration.In another illustrated embodiment, integrated piston head can use with bilateral shaft (through-shaft) damper designs.Yet the use of integrated piston head is not limited to these illustrated embodiment.
According on the other hand, oil hydraulic motor is integrated in the piston head of damper.Oil hydraulic motor has axle, and this axle extends through the generator of piston rod arrival on the opposition side of piston rod.In this embodiment, damper is configured to and traditional single-cylinder type structural similarity in addition.Alternately, the double barreled configuration that has the compression bypass can use with this oil hydraulic motor and electric motor/generator configuration.In another illustrated embodiment, can in the bitubular design with selectivity valve regulation accumulator, adopt relative motor/generator system.Yet the use of relative oil hydraulic motor electric motor/generator systems is not limited to these illustrated embodiment.
According to another aspect, oil hydraulic motor becomes whole with generator with the basic valve of damper.In one embodiment, the three cartridge type adjust system of using safety check, low pressure volume and high pressure volume have been adopted.In another embodiment, have with the double barreled design of the external volume that stretches the volume connection and can use together with selectivity valve regulation accumulator and integrated basic valve.Yet the use of basic valve system is not limited to these illustrated embodiment.
Other aspect relates to the kinematics character that dynamically changes the power generation damper.Can the amplitude that act on the power on the piston of damper be controlled to required level with controller.As example, according to a mode of execution, can control response, thereby the power/rate response of the automotive dampers that simulation is conventional (namely, damping), or in another example, a kind of mode of execution can comprise can be controlled to make the energy maximization that obtains from the wave input.Some aspects relate to from the energy that is produced by the power generation damper comes controller to self energy supply.This can allow wireless half ACTIVE CONTROL or full ACTIVE CONTROL.
Other aspect relates to the power generation damper that is assembled in the vehicle suspension system.This power generation damper can provide main damping source in suspension system.Yet the present invention is not limited to this on the one hand and can utilizes other application.For example, other aspect relates to the power generation damper that is mounted to industrial energy and obtains platform in---obtaining system such as the ocean surge energy---.
Referring now to accompanying drawing,, and at first referring to Fig. 1, Fig. 1 shows the mode of execution of the integrated piston head that comprises oil hydraulic motor and generator.This integrated piston head 1 is arranged on the oil hydraulic cylinder, wherein, in the above and below of piston head fluid is arranged all.When fluid when (with respect to the fluid of below) is pressurized above piston head, fluid flows to above piston head in one or more input/output end port 2.Although in the mode of execution of Fig. 1, adopt positive discharge capacity gerotor (Gerotor) 3 as oil hydraulic motor, the present invention is not limited on the one hand at this.When Fluid Flow in A passed input/output end port 2, pressure difference promoted gerotor mechanism 3 and rotates in its biasing cavity volume.Be connected to gerotor motor 3 transmissions generator shaft 8, this generator shaft 8 is connected to transmission again the generator 5 that is immersed in the hydraulic fluid, so that the rotation of oil hydraulic motor makes the generator rotation, and vice versa.Fluid flows through oil hydraulic motor 3 and flows out from the input/output end port below piston head (or a plurality of input/output end port) 4 from input/output end port 2.This rotates axle 8, and this axle 8 makes generator 5 rotate these generator 5 generation currents.Electric current is transmitted via being routed in the wire of the outer also wiring of piston head and damper housing by hollow piston rod 6.Sealing on the outer rim 7 of piston head has prevented that fluid from getting around input/output end port by flowing around piston head.When fluid is pressurized below piston head, fluid enters input/output end port (or a plurality of input/output end port) 4 below piston head, by oil hydraulic motor and from input/output end port 2(or a plurality of input/output end port of piston head top) flow out.
Fig. 2 shows the mode of execution of the alternative integrated piston head of the piston head shown in Fig. 1.In this embodiment, positive discharge capacity gerotor 16 is used as oil hydraulic motor, and the outer member 17 that they are different from mode of execution shown in Figure 1 to be gerotor motor 16 by generator shaft 19 transmissions be connected to generator 18, and the inner member 36 of gerotor motor 16 is in eccentric shaft 20 idle running.This layout be so that the outside larger diameter element of gerotor can be shared same low frictional torque bearing (such as deep groove ball bearing or analog) with the outside larger diameter element of generator shaft, and so that has the inner member of less inner diameter and can directly turn round at its axle.
In the application of damper, the speed of piston and therefore gerotor motor speed along a direction continuously acceleration/deceleration then stop, and subsequently along opposite direction acceleration/deceleration.In the situation that bound by theory not, along with the speed of gerotor slows down, lost any hydrodynamic lift on the sliding bearing that is created in gerotor, and applied higher frictional force at this bearing.The diameter of this bearing is larger, then the torque of the loss of friction by this increase is just more, and in this is used, when gerotor is used as motor, this torque loss may equal or even greater than the torque that is produced by motor self, thereby cause potentially the motor stall.Even produce hydrodynamic lift when having enough speed at this sliding bearing surface of contact place and therefore so that frictional force when significantly reducing, or in the situation that bound by theory not, diameter at the energy loss at this surface of contact place and 4 power is proportional, therefore it is desirable to keep the sliding bearing diameter as much as possible little of to reduce energy loss.Utilize the bearing arrangement of above-mentioned uniqueness, now larger outer member is by also will supporting with the low friction rolling element bearing that generator shaft is shared, and the sliding bearing surface of contact is positioned on the inner member of minor diameter, thereby the potential advantages of low initial start torque and lower power loss in high speed are provided.Although low frictional torque bearing is more expensive than slip hydrodynamic bearing, outside inner gear oil pump element can alleviate any cost increase with the fact that generator shaft is shared identical low frictional torque bearing.
By on the longitudinal center line that low frictional torque bearing is placed outside inner gear oil pump element or near this longitudinal center line, all or nearly all radial load that is produced by outside inner gear oil pump element is passed to low frictional torque bearing; This makes it possible to use cheaply sliding bearing in the opposite ends of generator shaft.As shown in Figure 2, the diameter of this sliding bearing 34 can be reduced to the size that is significantly less than outside inner gear oil pump element diameter, thereby reduces its frictional loss.
In mode of execution shown in Figure 2, integrated piston head 21 is disposed in the oil hydraulic cylinder, wherein in the above and below of piston head fluid is arranged.When fluid when (with respect to the fluid of below) is pressurized above piston head, in one or more input/output end port 22 that fluid flows in piston head 21 along flow path 23.When flow was crossed input/output end port 22, pressure difference promoted gerotor 16 and rotates at the axle journal 24 of the biasing of gerotor axle 20.Be connected to generator shaft 19 to outer member 17 transmissions of gerotor motor, this generator shaft 19 is connected to transmission again this generator 18 of generator 18(and is immersed in the hydraulic fluid) so that the rotation of oil hydraulic motor is rotated generator, and vice versa.Fluid flows to piston head below from input/output end port 22 by the input/output end port 25 oil hydraulic motor 16, the gerotor axle and the path 26 in the generator casing 27, as by shown in the flow path arrows 28.This Fluid Flow in A rotates gerotor, and gerotor makes again generator shaft 19 rotate, and generator shaft 19 makes generator 18 rotate generator 18 generation currents.In this embodiment, electric current is transmitted via the wire 29 of the piston rod 30 that is routed in the hollow of the outer and wiring of piston head and damper housing by being connected to generator casing 27 via high-pressure and hydraulic Sealing 31.Sealing 32 on the outer rim of piston head has prevented that fluid from getting around this input/output end port owing to flowing around piston head.When fluid is pressurized below piston head, fluid is via path 26 inflow generator shells 27 and enter input/output end port 25 in the gerotor axle 20, by oil hydraulic motor, and the input/output end port from piston head (or a plurality of input/output end port) 22 flows out.
Generator shaft 19 is supported by bearing 33 and 34 at the place, two ends, simultaneously the rotor 35 of axle 19 supporting outside inner gear oil pump elements 17 and generator 18.Inner gerotor element 36 is supported on the gerotor axle 20 via shaft bearing 24.The gerotor axle is also as cover plate, so that gerotor 16 is positioned between gerotor axle and the piston head 21 vertically. Hidden port 37 and 38 can be set, so that the gerotor assembly keeps the hydraulic axial balance in piston head and gerotor axle.
Shown in Fig. 2 A, the port 25 in the gerotor axle is exposed to the pressure in the generator casing 27 and centers on this port and do not have outer seal region.Owing to having pressure difference between the fluid in port 25 and the fluid in the generator casing 27, do not need outer seal region, and the zone that gerotor is had reduce contact can reduce the surface friction drag between the sealing surface of gerotor and gerotor axle.The opposed hidden port 37 that is present in the piston head also is the pressure that is exposed in the generator casing 27, does not therefore also have the outside seal band around this hidden port.This not only helps to make the gerotor retainer shaft to the hydraulic pressure balance, but also means when fluid-phase and flow into for the gerotor shell and during outflow port 25, fluid also will flow through hidden port 37.When fluid flowed into and flows out hidden port 37, fluid will flow through the rolling element of low frictional torque bearing 33, thereby the maintenance bearing moves in the fluid supply of constantly updating and any local pyrexia of the fluid that produces owing to frictional loss is minimized.
Shown in Fig. 2 B, outside inner gear oil pump element 17 by being connected to generator shaft with being fixed on driving pin 39 transmissions in the outer member.These pins are connected to generator shaft by the slit 40 of arranging around the outer dia of generator shaft.In one embodiment, these pins are for split ring pin type and not only driving torque is transferred to generator shaft from gerotor, but also as small-sized water-hammer arrester, thereby from the high frequency motion of damper, absorb the oscillating load that places gerotor.
Generator shaft has path 41, and this path 41 allows the stream from the port in the gerotor axle to enter in the generator casing 27 and from that by generator shaft to flow to the volume of piston head below.
Referring again to Fig. 2, generator shaft accommodates safety check 42, this safety check 42 allows to enter in the generator casing by the hidden port of gerotor, generator shaft, path the gerotor axle and enter free-flow the volume of piston head below from that from piston head, walks around gerotor so that the damping that has realized reducing in compression stroke (and the energy that reduces reclaims).Safety check activated by spring 43; Preload on spring can be adjusted so that compression damping can change to maximum value from minimum value, realizes whereby maximum compression damping, to be adapted to different application.This safety check will not allow to get around gerotor and flow in stretching stroke, make it possible to realize stretching completely damping (and energy recovery).
As shown in Figure 2, escape valve 44 can be used to limit the pressure maximum in the generator casing, and therefore limits the pressure maximum on the bottom side that is present in integrated piston head (IPH).The pressure that is present in the generator casing acts on the seal washer 45 via path 46.Seal washer is held to be resisted against on the sealing surface on the piston head by spring 47, thereby stops outflow pathway 46.The pressure that acts on the zone of path 46 has produced the power that seal washer is removed, and in case from the generator casing, making every effort to overcome of acting on the seal washer upward pressure taken the spring force that comes from spring 47, so the seal washer downside removing and allow to leave generator casing and therefore leave IPH, get around gerotor, via the slit 48(in the piston head shown in Fig. 2 A) arrive the flowing of upside of IPH.Spring force can change to change the pressure that escape cock is opened with the quantity that acts on the path on the seal washer, thereby is adapted to different application.
Escape cock is used to be limited in the pressure difference that is present under the high stretching, extension stroke on the whole gerotor, so that the stretching, extension damping force of not only restriction maximum, but also the top speed of restriction gerotor.This will remain to gerotor bearing and alternator speed in the rational limit under high stretching force, thereby improve the serviceability of IPH.
Fig. 3, Fig. 3 A, Fig. 3 B and Fig. 3 C show the mode of execution of integrated motor/generator unit (IMGU), this integrated motor/generator unit (IMGU) combines the feature of the mode of execution shown in Fig. 2, but is combined in the compacter unit that number of components reduces.This mode of execution can be used to during IPH shown in Fig. 4 A arranges, maybe can be as being bonded to the following damper of discussing with reference to Fig. 6 or independently ' valve ' in the actuator.As in aforementioned embodiments, IMGU can be used as generator or be used as the hydraulic power supply of electric liquid actuator.
In this embodiment, and as in mode of execution illustrated in fig. 2, the outer member of gerotor motor with the similar manner transmission shown in the mode of execution illustrated in fig. 2 be connected to generator 50, the inner member 51 of gerotor motor is in eccentric shaft 52 idle running.This layout is so that the outer member of gerotor can be shared same low frictional torque bearing 53 with the outer member of generator shaft 54, and be able to directly turn round at eccentric shaft 52 so that have the inside gerotor element of less inner diameter, thereby efficient and cost benefit as summarizing in mode of execution illustrated in fig. 2 are provided.In mode of execution shown in Figure 3, generator 50 now and gerotor motor 55 place concentricity and coplanarly, opposite with placing of going out as shown in Figure 2 concentricity and contiguously.This layout not only reduces length and the weight of whole packing, but also has reduced the quantity of assembly, thereby has reduced cost and increased simultaneously serviceability.Be connected to (by bonding or other suitable methods) generator shaft 54(shown in Fig. 3 B magnet 56 direct-drives of generator), perhaps can directly be connected to outside inner gear oil pump element 49, thereby have been eliminated independent rotor part.Two low frictional torque bearings 53 of support generator axle have been divided the radial load from outside inner gear oil pump element equally.Because present two bearings have been divided this load equally, the bearing life that can be greatly improved, thereby the serviceability of raising IMGU.In the mode of execution that has illustrated, the outer races 57 of low frictional torque bearing directly is formed in the generator shaft, has eliminated additional outer race parts, has reduced simultaneously the quality of IMGU and the rotary inertia of generator rotary assembled.
Gerotor cap 58 is positioned on each side of gerotor element and comprises the first flowing ports 59 and the second flowing ports 60; These ports can be ports that circulate fully or hidden according to the needs of using, and these ports are in the axial hydraulic state of equilibrium so that the gerotor assembly is placed as.The port configuration can be symmetrical about the center line of vertical center line and level.The gerotor cap is connected and is fixed to IMGU end cap 61.Be contained in flow passage 62 and 63 in the IMGU end cap and be connected to the first flowing ports and the second flowing ports in the gerotor cap, so that when fluid flows to another one from a port, the rotation of gerotor occurs.
By the symmetric configuration in conjunction with port arrangements, flowing into and flow out the flow path of hydraulic unit can be on the same side or opposition side on the IMGU, thereby has improved the use flexibility for different application.The valve that this symmetrical configurations of components also allows to add is connected such as by-pass valve, Decompression valves, accumulator etc. with connection---is positioned to relative with the second flowing ports with the first flowing ports, pass gerotor and center on flowing (namely of gerotor to allow to produce, travel to and fro between the first port and the second port), thus parallel flow path provided for hydraulic unit.Moreover this can also provide favourable encapsulation configuration.
By being positioned to generator gerotor motor 55 coplanar, with opposite around generator or contiguous generator, occurred now flowing into and flowing out flowing of hydraulic unit via the first port and the second port, center by generator, as shown in the mode of execution of Fig. 1 and Fig. 2.This shortening has also been simplified flow path, has reduced viscous loss, thereby has improved the efficient of unit.
Other valve---such as Decompression valves, by-pass valve and load holding valve etc. can be combined in the gerotor cap and or be combined in the IMGU end cap (or even in outside of IMGU end cap) so that other function to be provided, namely as generator again as actuator.
The inner race 64 of low frictional torque bearing be directly formed in the gerotor cap (or in IMGU end cap) and remain on vertically the gerotor cap and the IMGU end cap between.This is by having eliminated the needs of independent bearing inner race and further reduced the quantity of parts.In the mode of execution that illustrates, low frictional torque bearing is the bearing of cylindrical roller pattern, certainly, shown bearing arrangement can easily be changed in conjunction with the low frictional torque bearing of other types or even sliding bearing, confirm such as the application, because concrete application is not limited to this on the one hand.
In mode of execution as shown in Figure 3, eccentric shaft 52 keeps fixing with respect to the gerotor cap and inner gerotor elements relative rotates in the axle by plain friction bearing 65 supportings.Eccentric shaft is used to connect and location gerotor cap and IMGU end cap, and the IMGU assembly is threaded connection part 66 or other structures---such as squeezing forging and pressing processing and welding---and be fixed.Realized guaranteeing accurate interval between the gerotor cap by the shoulder 67 on the eccentric shaft, so that between gerotor and end cap, keep correct axial clearance, with suitably and effectively operate gerotor.
Be connected to stator 68 transmissions of generator outer sleeve 69(by bonding or other suitable devices), and this outer sleeve is sandwiched between two IMGU end caps so that this stator is concentricity and keep correct axially locating with the generator shaft maintenance.Timing feature between two IMGU end caps and outer sleeve make radially location relative to each other of IMGU end cap, with the correct timing of guaranteeing flowing ports and the correct location of eccentric shaft 52.
Because the compact feature of the integrated motor/generator unit shown in this embodiment, for IMGU, can be used as the plug-in type regeneration valve, this unit is placed in the machining hole of device or in the cavity volume whereby, so that flowing ports is about the first port and the alignment of the second port and the sealing of IMGU.Then can will flow by the counterelectromotive force of control generator is controlled in the oil hydraulic circuit, or this IMGU can be by supplying electric energy to generator so that hydraulic unit rotates and is used as hydraulic power supply, so that IMGU is used as pump.The possible purposes of this valve can be as the pressure governor or the Decompression valves that are used for larger oil hydraulic circuit.Usually, the pressure that the hydrovalve with controllable aperture is used in the oil hydraulic circuit is regulated, and therefore, and energy is owing to carrying out throttling and be wasted leading to the flow of wearing these apertures.By the IMGU of combination as the regeneration pressure control valve, these energy can be hunted down now.
Other application comprises variable hydraulic power supply, such as being used for motor or Lubricating oil pump of gearbox.Normally, these pumps have fixing discharge capacity and driven with certain axle speed.The size of these pumps is constructed to satisfy with any given axle speed the traffic demand of greatest hope, and therefore, and these pump supplies are than common required more flow, and the use of energy by flow control valve is wasted.Because compact build and the cylinder form of IMGU, it can be used for substituting these pumps, insert as simple insertion unit in the cavity of the machining in motor, the speed changer etc., or as the outside unit of installing.Because the control of the variable speed of IMGU and flow control ability therefore, requirement can be at any time accurately mated in the output of pump, thereby has reduced the energy consumption in these are used.
Fig. 4 and Fig. 4 A show the mode of execution of single-cylinder type damper 10, and it has adopted respectively the integrated piston head 1 of Fig. 2 and Fig. 3, yet IPH also can have configuration as shown in Figure 1.At this, integrated piston head 71 is disposed in the housing that comprises minimum cylinder volume 73 and stretching, extension volume 74.Additionally, the pressure of convection cell in floating piston 75 sealing gas-filled type accumulators 76 and the maintenance housing.When piston rod 30 stood jounce, fluid flowed into by integrated piston head 71 from minimum cylinder volume 73 and stretches the volume 74.During the jounce stroke, floating piston 75 moves with pressurized gas, makes it possible to compensate the volume that is introduced into the piston rod in the stretching, extension volume 74.During resilience, fluid flows into the minimum cylinder volume 73 by integrated piston head 71 from stretching volume 74.Simultaneously, thus floating piston 75 moves to enlarge accumulator gas volume 76 has compensated the piston rod volume that leaves housing during resilience.
When Fluid Flow in A passed through integrated piston head 71, oil hydraulic motor rotated, and the rotation of oil hydraulic motor makes the generator rotation.Be pushed through like this motion generation current of the fluid of piston head 71 from the motion by piston 30.The energy that comes from generator is transmitted via wire 29, and this wire 29 leaves IPH, by the piston rod 30 of hollow, and leaves the damper housing via boom end 77 at the place, end of piston rod and arrives outside.High pressure leadthrough 31 can be used to the conductor part that is immersed in generator in the hydraulic fluid is opened with the conductor part sealing of leaving piston rod arrival external environment condition.
By changing the electrical characteristic of generator, just can change the kinematics character of damper.If by using lower impedance so that the load on the generator increases at terminal, the power/rate feature of generator will be enhanced (power that every angular velocity is larger).Because oil hydraulic motor and generator are coupled, this is passed to oil hydraulic motor and therefore is passed to fluid path by integrated piston head.When lower impedance was applied to generator, linear relationship had caused the power on the damper piston/rate feature to increase, and when larger impedance was applied to generator, linear relationship had caused the power on the damper piston/rate feature to reduce.
Similarly, generator can be driven as motor, and oil hydraulic motor can be used as oil hydraulic pump.This allows the actuating of damper, thereby has produced the active linear actuator.With the mode of execution of Fig. 4 as an illustration the example of this usage of property example be to drive electric motor/generator 18 by applying voltage.As example, have the brush d.c. motor can be used as generator and Gerotor pump (Gerotor pump) can be used as oil hydraulic motor, yet the present invention is not restriction in this respect.When voltage is applied to generator 18, oil hydraulic motor mechanism will rotate, thereby according to direction (being subjected to the control of the polarity of voltage of the d.c. motor/generator) propelling fluid that rotates from minimum cylinder volume 73 to stretching volume 74, perhaps from stretching volume 74 to minimum cylinder volume 73.The motion pushing piston head of fluid from a volume to another volume moves, and makes to activate to get piston rod.In some applications, this can be usefully as the active suspension system in the vehicle, and with the dislocation controlled of permission wheel, thereby raising driving comfortability and landform are passed through characteristic.In the application of some industry, this can be usefully as the independently sealed hydraulic actuator with high power density characteristic.
In one embodiment, the gas in the accumulator 76 should be pressed into and make it possible to guarantee that maximum compression (jounce) damping is no more than by accumulator 76 is applied to power on the minimum cylinder volume 73.In one embodiment, pressure is usually at 200psi to 800psi(pounds/square inch) scope in, suitable numerical value can as described belowly calculate: the pressure of accumulator＞maximum jounce damping force/floating piston surface area.
The mode of execution of Fig. 4 A shows a kind of single-cylinder type damper that the IPH71 shown in Fig. 4 is the layout of mode of execution as shown in Figure 3.At this, IPH72 is connected to piston head 150, and piston head 150 is connected to piston rod 30.Sealing 151 is contained in the piston adapter, thereby allows IPH72 and other damper structure to share, and for example shares with damper structure illustrated in fig. 6.Certainly, the seal can directly be contained among the IPH71, and IPH can directly be connected to piston rod 30.
Described, comprise other feature in conjunction with some mode of executions of the single-cylinder type damper of integrated piston head 1.Some application---such as vehicle shock absorber---need minimum damping sometimes during jounce.Compare with the fluid path by oil hydraulic motor, in order to reduce the damping during the jounce, can be in conjunction with safety check " bypass " 42 in integrated piston head (or other positions), so that fluid can flow to the stretching, extension volume from minimum cylinder volume by by-pass valve, on the contrary but quite different.In addition, other valves---such as one-way valve, by-pass valve and escape valve 44---can be used to further adjust driving performance.
In some cases, it is desirable to, remove the gas-filled type accumulator and with low voltage operated system, thus the minimizing possibility that fluid is leaked by shaft seal.Additionally, generator being positioned to leave piston head is desirable (thereby for example with in the situation that uncompromising stroke of piston allows larger motor to adapt to Length Ratio).Fig. 5 has showed a kind of mode of execution of integrated power generation damper, and this integrated power generation damper operates with low pressure, and generator is located away from piston head, and this integrated power generation damper is take the compression bypass as feature.
The double barreled damper mode of execution of Fig. 5 has the piston head 81 that is arranged in the inner shell, and this inner shell comprises minimum cylinder volume 79 and stretches volume 80.In first mode, piston 81 moves through at least a portion of jounce stroke, so that the hydraulic fluid in the minimum cylinder volume 79 is pressurizeed.In the second pattern, piston moves through rebound stroke at least in part so that the hydraulic fluid in stretching volume 80 is pressurizeed.Hold low pressure volume 82 with the concentric urceolus of inner core.Low pressure volume 82 containing fluids and compressible medium (such as gas, foam or bubble).The piston head 81 that is arranged in the inner shell holds integrated oil hydraulic motor 83, and this integrated oil hydraulic motor 83 comprises the first port 84 and the second port 85.The first port 84 is communicated with minimum cylinder volume 79 fluids, and the second port 85 is communicated with stretching, extension volume 80 fluids.Piston rod 86 be hollow and hold axle 87, this axle 87 is connected the electric motor/generator 89 on another end of oil hydraulic motor 83 and piston rod 86 on the piston head 81.The rotation of oil hydraulic motor 83 causes the rotation of electric motor/generator 89.
In the mode of execution of Fig. 5, the resilience damping is provided by electric motor/generator 89 and transmits by the axle 87 in the piston rod 86.Resistance on the axle 87 is passed to oil hydraulic motor 83 and flows between minimum cylinder volume 79 and stretching, extension volume 80 with limit fluid.As discussed previously, the kinematics characteristic of damper can be changed by the variation of the electrology characteristic on the terminal that makes electric motor/generator.In addition, can be by supplying with power and drive on one's own initiative this system to electric motor/generator.
In the double barreled mode of execution of Fig. 5, during jounce, the pressurized fluid in the minimum cylinder volume 79 flows in the low pressure volume 82 by relief valve 90, and leaves safety check 91 arrival and stretch volume 80.In this embodiment, the volume of fluid that the volume ratio that enters the fluid of relief valve 90 is left safety check 91 is large, and this volume differences is stored in the low pressure volume by the compressible medium in the compression and low pressure volume.Except this fluid path, some fluids can enter to by piston head 81 from minimum cylinder volume 79 and stretch the volume 80, with generation current in generator 89 at the same time.
During resilience, the mode of execution of Fig. 5 will pressurize to the fluid that stretches in the volume 80, thereby safety check 91 cuts out.Fluid is pushed and flows into the minimum cylinder volume 79 by piston head 81 from stretching volume 80.Side by side, along with the compressible medium expansion in low pressure volume 82, the fluid that stores in low pressure volume 82 will flow in the minimum cylinder volume 79 by relief valve 90, to replace piston rod volume.Along with fluid from minimum cylinder volume 80 flow through port 85, enter the oil hydraulic motor 83, from port 84 out, enter and stretch in the volume 79, oil hydraulic motor 83 rotates.This makes at the axle 87 of piston rod 86 interior runnings and then motor/generator 89 and rotates, so that this Fluid Flow in A produces counterelectromotive force (EMF) so that damping to be provided from motor/generator.
In mode of execution shown in Figure 5, biasing ring 93 is used to piston rod 86 is attached to vehicle, yet, can adopt any suitable attachment method, such as adopting ring connector or threaded piston rod assembling set.In the system of Fig. 5, generator is arranged on the top for the mounting points of piston rod.Some mode of executions allow like this.In one embodiment, axle 87 passes shaft seal, and what this shaft seal made axle comprises fluid side and axle the air open side is separated.In an example, this allows to insert in the generator casing 92 that can be threaded onto on the piston rod with the axle 87 of key, with the main erection unit with the piston rod end that acts on damper.In another embodiment, the biasing link adapter is used on top and the bottom, realizes that bolton is attached to allow in the situation that damper is not carried out the sidepiece loading.At this, the entire length of axle 87 and generator 92 can be encapsulated in the fluid in manufacture process, has eliminated being used for the needs of field erected pressure axis Sealing.In another embodiment, adapter can be attached on the piston rod, does not need during installation machining screw on generator casing to allow eyelet mounting points or piston rod nut that attachment method is installed.Moreover this allows to eliminate the shaft seal of the generation friction on motor drive shaft 87.Although provided the some attachment methods that are used for the piston rod end of damper, yet the present invention is unrestricted on the one hand at this.
Fig. 6 has showed another mode of execution of integrated power generation damper, similar to mode of execution shown in Figure 5, this integrated power generation damper operates with low pressure and makes generator be positioned to leave piston head, and this integrated power generation damper is take the compression bypass as feature, different situations are: motor/generator is not arranged on the end relative with piston head of piston rod, but is oriented to vertical with cylinder body.This structure provides following benefit: overall impingement length shortens, and has eliminated the needs to elongated concentric shafts.This layout can be more suitable for using in vehicle shock absorber, and in vehicle shock absorber was used, it was affined that vibration length and encapsulation require.
The double barreled damper mode of execution of Fig. 6 comprises the piston 94 that is arranged in the inner shell, and this inner shell comprises minimum cylinder volume 95 and stretches volume 96.In first mode, piston 94 moves through at least a portion in the jounce stroke, so that the hydraulic fluid in minimum cylinder volume 95 is pressurizeed.In the second pattern, piston moves through rebound stroke at least in part, so that the hydraulic fluid in stretching volume 96 is pressurizeed.Comprised low pressure volume 97 with the concentric urceolus of inner core.Low pressure volume 97 containing fluids and compressible medium 98(are such as gas, foam or bubble).Integrated motor/generator unit (IMGU) 72 is positioned at the boom end place of damper.IMGU shown in Figure 6 is similar to IMGU shown in Figure 3, and comprises the first port 100 and the second port one 01, but it can be similar to Fig. 1 or IMGU shown in Figure 2.The first port 100 is communicated with low pressure volume 97 fluids, and the second port one 01 is communicated with stretching, extension volume 96 fluids.
The flow of valve 102 restriction discrepancy low pressure volumes 97 is so that fluid flows into the low pressure volumes 97 by valve 102 from minimum cylinder volume 95 during jounce.Valve 102 upwards provides required flow resistance the party, so that provide suitable jounce damping characteristic for application.During resilience, valve 102 allows from low pressure volume 97 to minimum cylinder volume 95 free-flow.
In the double barreled mode of execution of Fig. 6, during jounce, the fluid of the pressurization in minimum cylinder volume 95 flows in the low pressure volume 97 by valve 102, and flows among the IMGU72 by port one 00, and leave IMGU by port one 01, and flow in the stretching, extension volume 96.In this embodiment, the volume that the volume ratio of leaving the fluid of minimum cylinder volume 95 enters the fluid that stretches volume 96 is large, and this difference in volume is stored in the low pressure volume 97 by the compressible medium 98 of compression in low pressure volume 97.During the resilience, the mode of execution of Fig. 6 will flow through IMGU72 from stretching volume 96 via port one 01 and 102 with propelling fluid stream to stretching the pressurized with fluid in the volume 96, flow in the low pressure volume 97, and flow in the minimum cylinder volume 95 by relief valve 102.Side by side, along with compressible medium 98 expansions in the low pressure volume 97, the fluid that stores in low pressure volume 97 also will flow in the minimum cylinder volume 95 by relief valve 102, to replace piston rod volume.Get back to the minimum cylinder volume 96 along with fluid flows into the IMGU72 and flows out IMGU from port one 00 by port one 01 from stretching, extension volume 96, oil hydraulic motor 55 and generator 50 rotate.This is so that produce counterelectromotive force (EMF) damping to be provided and to have produced electric current, as describing from motor/generator in Fig. 2.As discussed previously, the kinematics characteristic of damper can change by the electrology characteristic on the terminal that makes electric motor/generator and change.In addition, can be by supplying with power and drive on one's own initiative this system to electric motor/generator.
In the mode of execution shown in Fig. 6, during jounce, fluid flows into the low pressure volume 97 by valve 102 from minimum cylinder volume 95, flows among the IMGU72 by port one 00 subsequently, leaves IMGU and flows into subsequently by port one 01 and stretch in the volume 96.The fluid that flows through IMGU during jounce will cause that motor 55 and generator 50 rotate, although and do not have counterelectromotive force and produce, because required low shock damping power, for application-specific, will cause too high jounce damping force from the parasitic loss of Fluid Flow in A and rotary component.In these are used, can be in conjunction with the bypass check valve 105 that low pressure volume 97 is communicated to minimum cylinder volume 96.This safety check will allow fluid directly freely to flow to minimum cylinder volume 96 from low pressure volume 97, thereby reduce the jounce damping force, but will not allow flow to get around IMGU between the resilience damping period.
In mode of execution shown in Figure 6, there is a certain amount of oil between the axle journal 104 of the cavity volume 103 that is trapped in piston 94 during the decline of jounce stroke and rebound stroke and end cap.When piston 94 bump so that axle journal 104 when entering in the cavity volume 103 (in jounce stroke or rebound stroke), is trapped in hydraulic fluid in the cavity volume 103 is pushed and flows out the annulus that is formed between axle journal outer diameter and the cavity volume inner diameter.The size of annulus is configured to produce pressure peak and acts on the cavity volume zone, provides hydraulic cushion thereby produce other power with the ending in jounce stroke and rebound stroke.Gap between cavity volume 103 and axle journal 104 can be selected such that to produce correct buffering capacity to adapt to application.
In some operational versions, it is desirable to have power generation damper as described below: this power generation damper is not subjected to the restriction of gas pressure in compression damping, have in compression and resilience and all catch the feature of energy, and make the length of stroke maximization of per unit body length.Now the some mode of executions in conjunction with above-mentioned feature are described.
According to mode of execution as shown in Figure 7, three cartridge type dampers in conjunction with energy harvesting IMGU are disclosed.In this embodiment, piston rod 105 and hydraulic jack type (solid) piston 106 are disposed in the internal flow filling cylinder 107.Inner shell (set minimum cylinder volume 108 and stretch volume 109) by with inner core 107 concentric second 110 center on.Space between inner core and second comprises high pressure volume 111.Second 110 by with second concentric the 3rd 112 surround.Space between second and the 3rd comprises low pressure volume 112.High pressure cylinder and low pressure cylinder can be put upside down in some embodiments.
In the mode of execution in Fig. 7, integrated motor/generator unit (IMGU) 72 is positioned at the place, end of the bar of damper.IMGU shown in Figure 7 is similar to IMGU shown in Figure 3, and alternatively, it can be similar to Fig. 1 or IMGU shown in Figure 2, and IMGU shown in Figure 7 comprises the first port 113 and the second port one 14.The first port 113 is communicated with high pressure volume 111 fluids, and the second port one 14 is communicated with low pressure volume 112 fluids.
During jounce, piston rod 105 pushing pistons 106 enter minimum cylinder volume 108, and this propelling fluid flows into the high pressure volume 111 by directional check valve 115 from minimum cylinder volume.This high pressure volume 111 is communicated with the first port 113 fluids of IMGU72.Fluid flows through the first port 113 from high pressure volume 111, by IMGU72, and from 14 outflows of the second port one, flows in the low pressure volume 112, passes directional check valve 116, flows into and stretches in the volume 109.Side by side, the compressible medium 117 in low pressure volume 112---such as abscess or bubble---compression is with the piston rod volume of dislocation introducing.
During resilience, piston rod 105 pulling pistons 106 enter and stretch volume 109, and this is tried hard to recommend moving fluid and flows into the high pressure volume 111 by directional check valve 118 from stretching volume.This high pressure volume 111 is communicated with the first port 113 fluids of IMGU72.Fluid flows through the first port 113 from high pressure volume 111, by IMGU72, and from 14 outflows of the second port one, flows in the low pressure volume 112, by directional check valve 119, and flows in the minimum cylinder volume 108.Side by side, 117 decompressions of compressible medium in the low pressure volume 112, the piston rod volume of withdrawing from replacement.
Flow into the IMGU72 along with fluid passes through port one 13 from high pressure volume 111, and get back to the low pressure volume 112 from port one 14 outflow IMGU, oil hydraulic motor 55 and generator 50 rotate.This is so that produce counterelectromotive force (EMF) from motor/generator, so that damping and generation current to be provided, as described at the mode of execution of Fig. 2.As discussed previously, the kinematics characteristic of damper can change by the electrology characteristic on the terminal that makes electric motor/generator and change.In addition, can be by supplying with power and drive on one's own initiative this system to electric motor/generator.
According to another mode of execution, Fig. 8 shows double barreled as described below design: this double barreled design is not subjected to the restriction of gas pressure, is captured as feature with bidirectional energy, and has the ratio of high stroke and body length.This system utilize Fig. 2, for the integrated piston head (although this also can be such as Fig. 1 or IPH illustrated in fig. 3) that double shell designs, wherein, guarantee that the whichever port is in the valve system that low pressure all is connected to accumulator always used to be operable to.Leading type valve or threeway pilot operated spool valve such as safety check can be finished this operation.Selector valve can guarantee that also the pneumatic accumulator 124 on the port that shares always is communicated with the low voltage side fluid of piston head.
In mode of execution as shown in Figure 8, integrated piston head 71 is disposed in the inner casing that holds hydraulic fluid.The stretching, extension volume 120 of inner casing is communicated with external fluid volume 121 fluids, and this external fluid volume 121 is contained between inner casing and the concentric outer shell.The two all links to each other minimum cylinder volume 122 and external fluid volume 121 with leading type valve group 123 fluids.Accumulator or the storage 124 of inflation also link to each other with leading type valve group 123 fluids.
During jounce, piston rod 30 is pushed in the cylinder, flows through oil hydraulic motor 16 with propelling fluid from minimum cylinder volume 122---this oil hydraulic motor 16 make electric motor/generator 18 rotate---and enter and stretch the volume 120.The electric current that comes from generator is walked along the wire at the center of passing piston rod 30.High-voltage conducting wires connects device from the fluid section of outside sealed inside oscillating body.Stretch in the volume because the jounce stroke is introduced piston rod volume, fluid need to be displaced to accumulator 124 from stretching volume, and this occurs by valve group 123.When minimum cylinder volume was pressurized, the leading type safety check 125 in the valve group 123 was opened by guide's circuit 127.Allow like this from accumulator 124 to stretch volume 120 flow freely and from stretching volume 120 to the flowing freely of accumulator 124, thereby the bar volume that allows to introduce is from stretching volume flow to accumulator 124.
During resilience, piston rod 30 is pulled out from cylinder, passes oil hydraulic motor 16 with propelling fluid from stretching volume 120---this oil hydraulic motor 16 rotates electric motor/generator 18---and be circulated to the minimum cylinder volume 122.Because rebound stroke is discharged piston rod volume from minimum cylinder volume, fluid need to be removed from accumulator 124, and this occurs by valve group 123.Because the bar volume will need to be displaced to the minimum cylinder volume from accumulator, the pressure in the minimum cylinder volume is less than the pressure in the accumulator, and this will allow fluid to flow into the minimum cylinder volume 122 by safety check 126 from accumulator 124.
In the embodiment shown, valve group 123 comprises safety check 126 and leading type safety check 125, being in low pressure with which mouthful of having guaranteed IPH all always is connected with accumulator, yet, this can also be by realizing such as slide-valve gear with other valve arrangements, and this slide-valve gear can switch being connected so that accumulator always is communicated with the low pressure volumetric fluid of accumulator 124 with stretching at minimum cylinder volume 122 between the volume 120.In this embodiment, during jounce, the pressure of pressure ratio in the minimum cylinder volume 122 in stretching volume 120 is large, and the inside pilot port that is connected to minimum cylinder volume 12 in the valve group 123 promotes changement, is communicated with so that fluid can and stretch between the volume 120 at accumulator 124.During resilience, the pressure of pressure ratio in minimum cylinder volume 122 in stretching volume 120 is large, and the inside pilot port that being connected in the valve group 123 stretched volume 120 promotes changement, so that fluid can be communicated with between accumulator 124 and minimum cylinder volume 120.Selector valve mechanism, other leading type valves and the valve (comprising mechanically actuated valve and the valve of electric actuation) that optionally connects based on pressure reduction and different fluid displacement are known in the prior art, and unrestricted in the present invention.
Although oil hydraulic motor 16 and electric motor/generator 18 are shown in integrated piston head 71 configurations, but the mode of execution of Fig. 8 can also be made of electric motor/generator configuration, piston head and the piston rod of Fig. 5, wherein piston head comprises oil hydraulic motor, piston rod comprises the inner rotation axle, and electric motor/generator is on the opposition side of piston rod.In another embodiment, the system of Fig. 8 can by the solid piston head and be placed in such as the base portion place of the damper of the disclosed system of Fig. 6 and at its outside oil hydraulic motor and generator to consisting of.At this, the first port of oil hydraulic motor can be communicated with minimum cylinder volume 122 fluids, and the second port can be communicated with (by external fluid volume 121) with stretching, extension volume 120 fluids.The remainder that comprises the system of valve group 123 can still keep as shown in Figure 8.
Some commercial Application of the hydraulic linear energy producing unit of sealing allows to be different from the alternative form factor of common automotive dampers.In the mode of execution of Fig. 9, show the integrated piston head of axis system.In this embodiment, integrated piston head 128 is arranged in the cylinder that comprises hydraulic fluid, and is connected to first piston bar 129 and the second piston rod 130.Piston head shown in Figure 9 is similar to piston head shown in Figure 3, but it can be similar to Fig. 1 or piston head shown in Figure 2.In some embodiments, the second piston rod 130 of separating device can be connected to spring mechanism, so that another piston rod is returned to common compressive state.
During the piston rod stroke on the first direction, be pushed and flow through oil hydraulic motor 132---this rotates electric motor/generator 133---and be circulated in the second volume 134 from the fluid of the first volume 131.The electric current that comes from generator is walked along the wire that passes one of them piston rod center, and wherein, high-voltage conducting wires connects device from the fluid section of outside sealed inside oscillating body.
During the piston rod stroke on the second direction, be pushed and flow through oil hydraulic motor 132---this rotates electric motor/generator 133---and be circulated in the first volume 131 from the fluid of the second volume 134.
Internal system is the device that changes for the fluid volume that transfering fluid causes owing to temperature fluctuation with compensation.In the mode of execution of Fig. 9, it is shown as the compressible abscess in the crack 135 that is inserted into therein in the piston rod 134.Yet the placement of fluid compensation mechanism can be or outside other positions inner in the unit.Additionally, accumulator especially can be used as substitute or the addition of foam, with transfering fluid.In some described modes, it is desirable that the pressure that the convection cell compensation mechanism meets with limits.In these mode of executions, can adopt as described in Figure 8 selector valve.
In some applications, such as in military heavy-duty vehicle, it is desirable having the energy harvesting rotation damper.The mode of execution of Figure 10 has been showed a kind of like this system, and wherein, integrated motor/generator unit (IMGU) is connected to rotation damper unit 136.In illustrated embodiment, IMGU72 is to illustrated in fig. 3 similar, but it also can be similar to Fig. 1 or IMGU shown in Figure 2.During the damper punch advance on the first direction, be pushed and flow to the first port 59 from the fluid of the first volume 138, flow out by oil hydraulic motor 55 and by the second port 60, enter in the second volume 139.Along with Fluid Flow in A passes motor 55, motor and generator rotate and generation current, as described in Figure 7.During the damper punch advance on the second direction, be pushed and flow to the second port 60 from the fluid of the second volume 139, by oil hydraulic motor 55, and flow out by the first port 59, flow in the first volume 138.Along with Fluid Flow in A passes motor 55, motor and generator rotate and generation current, as described in Figure 7.Be used for transfering fluid and can be combined in inside or outside in the mode of especially compressible abscess or accumulator with the device that compensates the fluid volume change that causes owing to temperature fluctuation.
In illustrated embodiment, IMGU is shown as the external means of rotation damper, yet, IMGU can be readily integrated into rotation damper mechanism in, thereby reduced whole plant bulk and eliminated outside hydraulic connecting.
Can adopt other rotation damper configuration, and because the present invention does not limit on the one hand at this, energy harvesting IPH or IMGU can be combined in these devices.
Some commercial Application of electro-hydraulic linear actuators provides the ability of catching energy in the direction opposite with its actuating, in the jacking equipment that is enhanced and is lowered subsequently in quality.In the mode of execution shown in Figure 11 and Figure 11 A, presented a kind of double barreled energy harvesting electro-hydraulic linear actuators, it can be caught energy and provide energy to actuation motion in stretching stroke in compression stroke.
In mode of execution as shown in figure 11, the IPH valve is arranged on the base portion place of actuator and concentricity with actuator, the IPH valve can be positioned at the base portion place of actuator body, but vertical with the axis of actuator, as shown in the mode of execution as shown in Figure 11 A, (this IPH valve also can be arranged on the base portion place of actuator body, but parallel with the axis of actuator).This can provide the packing advantage in the important application of the length of some actuator.
The double barreled mode of execution of Figure 11 and Figure 11 A has piston 140, and piston 140 is arranged in the inner shell 141 that comprises minimum cylinder volume 142 and stretching, extension volume 143.In first mode, minimum cylinder volume 142 is pressurized, makes piston 140 move through at least a portion that stretches stroke to overcome power.In the second pattern, piston moves through compression stroke at least in part by power the hydraulic fluid in minimum cylinder volume 142 is pressurizeed.Comprise the low pressure volume 145 that is communicated with the stretching, extension volumetric fluid by path 146 with inner core 141 concentric urceolus 144.Low pressure volume 145 comprises fluid and compressible medium 147(such as gas, foam or bubble).Integrated piston head (IPH) assembly 71(is 72 in Figure 11 A) be positioned at the base portion place of actuator.This IPH assembly can be similar to Fig. 1, Fig. 2 or IPH assembly shown in Figure 3, and comprise the first port 148 and the second port one 49.The first port 148 is communicated with minimum cylinder volume 142 fluids and the second port one 49 is communicated with low pressure volume 145 fluids.In the double barreled mode of execution of Figure 11 and Figure 11 A, between extensin period, supply with power for electric motor/generator 18, electric motor/generator 18 and oil hydraulic motor 16 are rotated, this has caused that fluid flows to the minimum cylinder volume 142 by port one 48 from oil hydraulic motor.Thereby in minimum cylinder volume, produced like this pressure generation power on piston 140, and then overcome the power that is present on the piston rod, so that piston stretches out.Along with piston stretches out, fluid passes low pressure volume 145 from stretching volume 143 transfers and flowing, and passes the low voltage side that the second port one 49 flow to oil hydraulic motor 16.In this embodiment, enter minimum cylinder volume 142 fluid mention less than the volume that leaves the fluid that stretches volume 143, and this volume differences storage volumes cancellation from low pressure volume 145 by making compressible medium 147 expansions in the low pressure volume 145.
Can load maintaining valve (such as safety check) be set to eliminate the leakage of passing oil hydraulic motor when actuator is in load maintenance operator scheme between the first port 148 and the minimum cylinder volume 142.This will prevent that piston from retracting and cause security risk in load maintenance situation.The load maintaining valve can be for leading type, electronics action or machinery action, in the prior art these valves be well-known and this patent unrestricted at this face.
In this embodiment, the retraction of piston can realize in two ways, in first mode, has external load (for example when actuator is used to reduce useful load) at piston rod; Piston will be retracted under the effect of this power.If used the load maintaining valve, make this valve events allowing before fluid flow to the first port 148 from minimum cylinder volume 142 so, piston can not retracted.In case this valve events (by electronic equipment, mechanical device etc.), fluid will flow to the first port 148 from minimum cylinder volume 142 subsequently, because load places on the piston rod, will cause that motor 16 rotates.This will cause that thereby generator 18 rotates from motor/generator and produce counterelectromotive force (EMF) so that the resistance that this is flowed to be provided, and as at the described generation current of Fig. 2.Controller can provide the impedance of variation to generator, thereby the control fluid flow to the speed of the first port from minimum cylinder volume, thereby the mode that reduces useful load controlled and safety is provided.
There is not useful load to act in the second pattern on the actuator, this piston is contracted in the following way: cause that by giving electric motor/generator 18 power supplies electric motor/generator 18 and oil hydraulic motor 16 rotate, this causes that fluid flow to the first port 148 from minimum cylinder volume 142, so that to low pressure volume 145 and 143 pressurizations of stretching, extension volume, thereby so that piston 140 retractions.Although this will need the low pressure volume pressurized, but because it only needs to overcome the friction of actuator and any subsidiary mechanism, therefore in this application, make the load of piston-retraction will be very little, in the limit of the compressible medium that the pressure that for this reason obtains in the low pressure volume will comprise in the low pressure volume.If adopt as mentioned above the load maintaining valve, before piston-retraction, the actuating of this valve will at first must be carried out so.
During the retraction of piston, fluid will flow into the first port 148 from minimum cylinder volume 142, pass motor 16, flow in the low pressure volume 145, flow through the second port one 49 and will flow to and stretch in the volume 143.In the embodiment shown, it is large that the volume ratio that is shifted by minimum cylinder volume enters into the volume that stretches volume, and this volume differences is stored in the low pressure volume 145 by the compressible medium 147 in the low pressure volume 145 is compressed.
Some application of energy harvesting electro-hydraulic linear actuators as shown in the mode of execution of Figure 11 and Figure 11 A may need to add other valve, such as pressure reduction safety valve and temperature difference safety valve etc.Be well-known in the prior art that is combined in such actuator of these valves, and this patent is unrestricted at this face.
In some energy harvesting is used, be favourable no matter how the direction of stroke keeps the motor/generator assembly in identical direction rotation.For these application, the motor/generator assembly can be connected to actuator (it is for linearity or rotary-type) by the rectifying valve loop.In the mode of execution that goes out as shown in figure 12, presented the energy harvesting linear actuators that is connected to integrated motor/generator assembly by the rectifying valve loop.In illustrated embodiment, rectifying valve loop 150 is the form of four safety check, yet identical function can realize by the use of pilot operated spool valve etc. certainly, and this patent is unrestricted at this face.
In shown mode of execution, integrated motor/generator assembly is to shown in Figure 3 similar, but it can be similar to Fig. 1 or integrated motor/generator assembly shown in Figure 2, and it comprises the first port 151 and the second port one 52.The first port 151 is communicated with the waste side fluid of commutating circuit and the second port one 52 is communicated with the side liquid that returns of commutating circuit.In shown mode of execution, linear actuators is the form of double barreled structure, and it has the first port 153 that is connected with the extend side fluid of actuator and the second port one 54 that is connected with the compressed side fluid.Piston 155 is arranged on and comprises in the inner shell that stretches volume 156 and minimum cylinder volume 157.In first mode, piston 155 moves through at least a portion of stretching in the stroke so that the hydraulic fluid that stretches in the volume 156 is pressurizeed.In the second pattern, piston moves through compression stroke at least in part so that the hydraulic fluid in the minimum cylinder volume 157 is pressurizeed.Be connected minimum cylinder volume 157 to second port ones 54 with the concentric urceolus of inner core.
Commutating circuit be configured as so that during stretching stroke from the first port discharging of actuator or during compression stroke, will always be introduced to the waste side of commutating circuit and introduce the first port of IMGU72 from the fluid of the second port discharging, the fluid that emits from the second port one 52 of IMGU will always be introduced to the second port one 54 at the first port 153 that is introduced to actuator during the compression stroke or during stretching stroke.This will guarantee no matter actuator is to stretch or retraction, and the sense of rotation of motor/generator all will remain unchanged under the effect of load.
Accumulator or storage 158 are connected to the second port one 52 of IMGU72 to regulate the difference in volume that stretches stroke and compression stroke.Storage is connected to the symmetrical ports relative with the second port one 52 in shown mode of execution, but it can be connected to along the return route of commutating circuit Anywhere.
Use a problem of commutating circuit to be in the energy harvesting actuator, motor/generator can not backdrive actuator, and motor/generator can " free-wheel " under specific inertia condition.But, this can overcome in the following manner: replace safety check (or guiding valve) with leading type valve (electric operation or mechanically operated), the order of arrangement of valves is so that be connected with the first port 153 fluids of actuator from the discharging of oil hydraulic motor by the first port 151 subsequently, similarly the second port one 52 of oil hydraulic motor is connected with the second port one 54 fluids, and vice versa.
Such as commercial Application, Military Application and aerospace applications and so on some be applied in pressure capability and the efficient aspect needs the hydraulic power of superior performance to supply to transmit required power density.In the mode of execution of Figure 13 and Figure 13 A, show integrated motor/generator unit, this integrated motor/generator unit comprises the axial piston unit of locating with generator concentricity and coplanarly.This mode of execution is to illustrated in fig. 3 similar, but hydraulic unit is axial plunger unit (being inclined disc type unit) now, and is opposite with Gerotor pump.When comparing with the oil hydraulic pump of other types, swash plate operated pump can be provided in the high-performance of P-V, speed, efficient and serviceability aspect.
In shown mode of execution, be connected to the magnet 161 of generator 162 and be supported end cap 164 and 165 by bearing 163 to cylinder body 160 transmissions of axial plunger unit 159.End cap 163 comprises the first port 166 and the second port one 67, the first ports 166 and the second port one 67 and is configured to coil to guide flow to pass through path 168 turnover cylinder bodies 160 as connection.Wobbler 169 is positioned on the end cap 165 on the contrary with cylinder body path 168.A plurality of plungers 170 are accommodated in the inner diameter of cylinder body 160 and by plunger piston slippery boots 171 and are held against wobbler.Well-known plunger is held against wobbler and is pushed and passes in and out the method for cylinder diameter in the prior art, and limit these actions not in the scope of this patent, similarly, cylinder body also is known against the method that the connection dish is loaded (by spring or other devices).
When electric energy is fed in the generator, generator will and cause cylinder body 160 rotations as electric motor, and the rotation of cylinder body 160 will cause again the suction action by plunger 170, and will occur to flow by the first port and the second port.The direction that flows will depend on the sense of rotation of cylinder body, and the sense of rotation of cylinder body depends on again the sense of current that is transported in the electric motor.On the contrary, if the first port or the second port are pressurized, the axial plunger unit will serve as motor and will rotate under this pressure difference so, and its rotation was and for example before described passes through generator and generation current.
By the speed of control electric motor, can in the situation of the mobile discharge capacity that needn't change the unit, change speed and then the flow rate of axial plunger unit.A lot of modification that have the variable displacement axial piston pump, and simultaneously they have and can control the advantage of flow rate to satisfy the demands, they all have the shortcoming that reduces when its discharge capacity its volumetric efficiency close to zero time.
---its size size identical with the variable displacement axial piston pump or variable ratio discharge capacity axial piston pump is little---the mobile discharge capacity that can provide variable flow rate to remain on simultaneously its maximum that makes the benefit of the concentricity and coplanar setting of axial plunger unit and motor/generator as follows: axial piston pump, thereby kept its swept volume.
In some operational versions, it is desirable having power generation damper as described below: be not subjected to the restriction of gas pressure in compression damping; In compression and resilience, all to catch energy as feature.Now in connection with above-mentioned feature the mode of execution shown in Figure 14 and Figure 14 A is described.
According to Figure 14 and the shown mode of execution of Figure 14 A, the three cartridge type damper designs of being combined with energy harvesting IMGU are disclosed.In this embodiment, piston rod 172 is arranged in the internal flow filling cylinder 174 with hydraulic jack type (solid) piston 173.Inner shell (set minimum cylinder volume 175 and stretch volume 176) by with inner core 174 concentric second 177 center on.Space between inner core and second comprises high pressure volume 178.Second 177 by with second concentric the 3rd 179 surround.Space between second and the 3rd comprises low pressure volume 180.High pressure cylinder and low pressure cylinder can be put upside down in some embodiments.
In the mode of execution of Figure 14, integrated motor/generator unit (IMGU) 72 is along the other base end part place that is positioned at damper of side, and in the mode of execution of Figure 14 A, integrated motor/generator unit (IMGU) 72 is positioned at the base end part place of damper.Similar to shown in Fig. 3 of Figure 14 and the shown IMGU of Figure 14 A, alternatively, it can be similar to the IMGU shown in Fig. 1 or Fig. 2, and Figure 14 and the shown IMGU of Figure 14 A comprise that the first port 181 and the second port one 82, the first ports 181 are communicated with high pressure volume 178 fluids and the second port one 82 is communicated with low pressure volume 180 fluids.
During jounce, piston rod 172 pushing pistons 173 enter minimum cylinder volume 175, fluid in minimum cylinder volume 175 is directed safety check 183 to be stoped and can not flow in the low pressure volume, and this fluid is pushed from minimum cylinder volume 175 and flow to and stretch in the volume 176 by being included in directional check valve 184 piston 173.Because the volume that the volume of the volume ratio that is transferred in the pressing chamber by piston rod 172 creates in stretching the chamber is large, this difference in volume enters into the first port 181 of IMGU72 by high pressure volume 178, and flow out from the second port one 82, flow in the low pressure volume 180.Simultaneously, the piston rod volume introduced with dislocation of the volume compression such as the compressible medium 185 of abscess or bubble or gas and so in low pressure volume 180.
During resilience, piston rod 172 pulling pistons 173 make it enter stretching, extension volume 176, fluid in stretching volume 176 is directed safety check 184 preventions and can not flow in the low pressure volume, and this fluid is pushed from stretching volume flow to high pressure volume 180.High pressure volume 180 is communicated with the first port 181 fluids of IMGU72.Fluid passes the first port 181 from high pressure volume 180, passes IMGU72, and from the second port one 82 out, flow in the low pressure volume 180, passes directional check valve 183, and flow in the minimum cylinder volume 175.Side by side, along with passing directional check valve 183 from low pressure chamber 180, fluid flow to the minimum cylinder volume compressible medium 185 decompressions in low pressure volume 180, thereby the piston rod volume that displacement is withdrawn from.
Flow to the IMGU72 along with fluid passes mouth 181 from high pressure volume 178, then by mouth 182 from IMGU out, return and flow in the low pressure volume 180 oil hydraulic motor 55 and generator 50 rotations.This is so that produce counterelectromotive force (EMF) so that damping and generation current to be provided from motor/generator, as described at the mode of execution of Fig. 2.As discussed previously, the kinematics characteristic of damper can be modified by making the electrology characteristic variation on the terminal of electric motor/generator.In addition, the damping force of this system can be raised to and surpasses by being in the scope of the damping force that counterelectromotive force provides under the power regenerating pattern by supply with power to electric motor/generator, or the damping force that is provided by the resistance from the system open loop parasitic loss is provided.Motor/generator can be driven into so that the fluid that flows from damper from the fluid antagonism of hydraulic motors in compression or resilience, thereby improved damping force, or motor/generator can be driven into so that in compression or resilience from the auxiliary fluid that flows from damper of the fluid of hydraulic motors, thereby reduce damping force.Motor/generator can also be driven into so that the fluid that flows from damper from the fluid antagonism of hydraulic motors reaches the static degree of damper maintenance that makes.Yet in this embodiment, damper can not be driven on one's own initiative so that damper will stretch or retracts owing to the power that is supplied to motor/generator.Yet the present invention is unrestricted in this regard, and for example when using in the single-cylinder type configuration, and in the situation that does not have other valve configuration, damper can stretch and retracts owing to the power that is supplied to motor/generator.In three cartridge types are arranged, damper stretches if motor/generator is driven, the mobile fluid that leaves the second port one 82 will freely flow and pass safety check 183 and 184, backflow is moved into the first port 181, if and motor/generator is driven and damper is retracted, the fluid that leaves the first port 181 that flows so will pressurize to stretching chamber 176, and then to pressing chamber 175 pressurizations, yet safety check 183 leaves prevention any retraction of flowing thereby not allowing piston rod of pressing chamber.
In some operational versions, can power stretches on one's own initiative to motor/generator or the retraction damper is desirable by supplying with, and according to mode of execution may needs other valve.Mode of execution shown in Figure 15, that be combined with other valve will be described now.According to mode of execution shown in Figure 15, disclose and the similar three cartridge type damper designs in conjunction with energy harvesting IMGU72 shown in Figure 14 (what alternatively, it can be to shown in Figure 14 A is similar).In this embodiment, Controlled valve 186 and 187 combinedly comes in to allow damper to pass through to supply with power and stretched on one's own initiative or retract to motor/generator.Controlled valve 186 and 187 can be controlled with the mode of electronics, the mode of hydraulic pressure or other mode.
When damper needed to be stretched, electric energy was supplied to motor/generator so that there is the fluid that flow to hyperbaric chamber 178 from the first port 181 of IMGU72.Controlled valve 186 is held to close and controlled valve 187 is opened to allow fluid 178 to flow to pressing chamber 175 from the hyperbaric chamber.Safety check 183 cuts out to stop from pressing chamber 175 to low pressure chamber 180 flow.Because hyperbaric chamber 178 with stretch volume 176 fluids and be communicated with, pressure will be present on the extend side and compressed side of piston 173 now simultaneously, and poor owing to the area---area that is equivalent to piston rod is identical---on the whole piston, piston rod will stretch.Along with piston extension, fluid by hyperbaric chamber 178 and controlled valve 187, is transferred to pressing chamber 175 from stretching volume 176, and fluid will flow to from low pressure chamber the second port one 82 of IMGU72 simultaneously, thereby make compressible medium 185 step-downs in the low pressure chamber.
When damper need to be contracted, electric energy was supplied to motor/generator so that there is the fluid that flow to hyperbaric chamber 178 from the first port 181 of IMGU72.Controlled valve 187 is held to close and controlled valve 186 is opened so that pressing chamber 175 is communicated with low pressure chamber 180 fluids, gets around safety check 183.Because minimum cylinder volume 175 is communicated with low pressure chamber 180 fluids now, the pressure difference on the whole piston will exist, thereby make piston-retraction.Along with piston-retraction, fluid will flow to low pressure chamber 180 and flow to the second port one 82 of IMGU72 from pressing chamber 175.Because the volume ratio of pressing chamber 175 stretches the volume of the large bar of volume of chamber 176, this difference in volume will flow to low pressure chamber 180 from pressing chamber 175, thereby the compressible medium 185 in the low pressure chamber 180 is compressed.
In some embodiments, integrated system disclosed herein can be combined with passive damping, and passive damping or in parallel with by-pass valve is perhaps connected with oil hydraulic motor.In the prior art well-known passive valve configuration, common bonding pad storehouse, directional valve and spring-loaded fluid restricted entry.Bypass path can allow the lower damping of damping that can allow than the viscous loss of passing oil hydraulic motor, or allows to adjust trickle driving performance, yet the present invention is unrestricted in this regard.Consider higher damping rather than, the valve configuration of series connection can allow than the generator higher damping of damping that (with very high speed) can provide under fully saturated state, and this is the requirement that is even more important in such as military damper in heavily loaded use occasion.Damping in parallel or series connection can directly be combined on the piston head in the by-pass pipe externally, in basic valve or other places.
In some applications, the dynamic range that can rationally be provided by oil hydraulic motor and generator can be provided the required dynamic range of damper.In this application, integrated system disclosed herein can with one or more initiatively/controlled valve is combined with, these valves are in parallel with oil hydraulic motor or connect (or parallel connection and serial connection combination) use.In one embodiment, one or more active/controlled valve can use individually or be combined with one or more passive valve.Initiatively/controlled valve can be suitable for predetermined pressure operation.Pressure that should be predetermined changes according to the action need of damper, oil hydraulic motor or generator.In addition, this pressure can be selected as dynamically improving or reducing the damping scope, and the damping scope that can be provided by oil hydraulic motor and generator is provided this damping scope.One or more active/controlled valve can electrically be controlled or the mechanically actuated or hydraulic machinery by some form activates to control.In addition, one or more active/controlled valve can be suitable for the Fluid Flow in A that provides unidirectional.By with oil hydraulic motor controlled valve being set in parallel, reduce damping force thereby can get around the viscous loss that oil hydraulic motor passes oil hydraulic motor by reduction by outside controllable device guiding fluid.By controlled valve in series is set, thus can flow into by the controllable device limit fluid of outside oil hydraulic motor or the efflux pressure motor make the damping force that damping force increases to can be provided in complete saturation state above generator.These valves can directly be combined on the piston head, and are local in basic valve outside or other.
Device be used as actuator rather than energy harvesting damper or be used as actuator and some mode of executions of energy harvesting damper in, can be in conjunction with other control valve, such as load maintaining valve, pressure limit valve etc., use required difference in functionality to provide.
According to some mode of executions, controller can provide impedance with based on the force-responsive such as the various parameters such as speed or position control damper to generator, and catches simultaneously the energy that is associated with motion in the damper.Force-responsive can be followed formula or based on the look-up table of these parameters.Because the amount of damping is controlled, but system do not activated, so the level of this control is called as semi-active damper.In other use occasions, the electric motor/generator in the damper can activated and allow completely ACTIVE CONTROL.
In some embodiments, integrated system disclosed herein can use in spontaneous mode, and in this mode, controller obtains electric power from the energy harvesting damper.This allows semi-active damper device, or allows in some embodiments generation current and use this electric current that the active damper of electric power is provided to himself control circuit.This system can allow with improve half initiatively or suspension fully initiatively easily improve vehicle and need not along the vehicle chassis cabling.In one embodiment, boottrap capacitor relies on the output of power generation damper.When the damper generation current, give capacitor charging.Simultaneously, the input of the electric power of controller is connected with this Parallel-connected Capacitor.In case boottrap capacitor reaches the specific voltage critical value, controller is opened and is begun and by the electric current that utilizes damper self to produce the kinematics characteristic of damper controlled.Capacitor or little battery can be used in the input of controller to filter the transient voltage input.
Should be understood that, in many mode of executions, system described here can be combined with to compress with spring mechanism or the extend piston bar.
Should be understood that, use for vehicle, shown mode of execution can be according to using required being configured as damper or as the slide column type damper.
Claims (166)
1. energy recycle device comprises:
Piston head, described piston head have the first side and the second side, and described piston head is suitable for being disposed in the housing of fluid filling, thereby are immersed in the described fluid;
Oil hydraulic motor, it is whole that described oil hydraulic motor becomes with described piston head, wherein, described oil hydraulic motor has the first port and the second port, described the first port and the fluid communication that is adjacent to described first side of described piston head, described the second port and the fluid communication that is adjacent to described second side of described piston head; And
Generator, described generator functionally is connected to described oil hydraulic motor.
2. energy recycle device according to claim 1, wherein, described oil hydraulic motor is gerotor.
3. energy recycle device according to claim 2, wherein, described gerotor further comprises the outside inner gear oil pump element that functionally is connected to described generator.
4. according to 1 described energy recycle device in the claim, wherein, it is whole that described generator becomes with described piston head.
5. energy recycle device according to claim 1 comprises that also piston rod and the electric wire of hollow, the piston rod of described hollow comprise passage and functionally be attached to described piston head, and described electric wire passes described channel routing and is electrically connected to described generator.
6. energy recycle device according to claim 1, wherein, described oil hydraulic motor and described generator are basically concentric.
7. energy recycle device according to claim 1, wherein, described oil hydraulic motor and described generator are basically coplanar.
8. energy recycle device according to claim 1, wherein, described oil hydraulic motor and described generator are basically coplanar and basically concentric.
9. energy recycle device according to claim 1 also is included as the bearing that described oil hydraulic motor and described generator share.
10. energy recycle device according to claim 1 also comprises water-hammer arrester, and described water-hammer arrester functionally is connected to described generator with described oil hydraulic motor.
11. energy recycle device according to claim 10, wherein, described water-hammer arrester comprises the open type spring pin.
12. energy recycle device according to claim 1, wherein, described piston is suitable between primary importance and the second place mobile, no matter described piston is that the sense of rotation of described oil hydraulic motor remains unchanged mobile between described primary importance and the described second place or mobile between the described second place and described primary importance.
13. energy recycle device according to claim 1, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
14. device according to claim 13, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
15. device according to claim 13, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
16. device according to claim 13, wherein, described at least one hydrovalve is electronic control valve.
17. energy recycle device according to claim 1 wherein, activates described oil hydraulic motor and described generator along the Fluid Flow in A of first direction, and activates described oil hydraulic motor and described generator along the Fluid Flow in A of second direction.
18. energy recycle device according to claim 1, described energy recycle device combines with the single-cylinder type damper.
19. energy recycle device according to claim 1, described energy recycle device combines with the double barreled damper.
20. energy recycle device according to claim 1, described energy recycle device combines with three cartridge type dampers.
21. energy recycle device according to claim 1 also comprises the controller that functionally is connected to described generator.
22. energy recycle device according to claim 21, wherein, described controller is at least in part by described generator powered.
23. energy recycle device according to claim 21, wherein, described controller outputs to external loading with energy from described generator.
24. energy recycle device according to claim 21, wherein, described controller is suitable for controlling Fluid Flow in A by described oil hydraulic motor by the electrology characteristic of controlling described generator.
25. energy recycle device according to claim 24, wherein, described electrology characteristic is the electromotive force of described generator.
26. energy recycle device according to claim 24, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
27. energy recycle device according to claim 1, wherein, described generator is controlled so as to and is driven as motor, and described oil hydraulic motor is driven as oil hydraulic pump.
28. energy recycle device according to claim 1, wherein, at least one in described piston head, described oil hydraulic motor and the described generator is suitable for providing damping force.
29. a device comprises:
Oil hydraulic motor, described oil hydraulic motor are suitable for being immersed in the fluid, and wherein, described motor has the first side;
Sealing strip, described sealing strip partly covers described first side of described oil hydraulic motor, wherein, the capped part of described first side of described oil hydraulic motor is sealed, and the not capped part and described fluid communication of described first side of described oil hydraulic motor.
30. device according to claim 29, wherein, described the first side described capped defines hidden port.
31. device according to claim 29, wherein, described oil hydraulic motor is gerotor.
32. device according to claim 29, wherein, it is whole that described oil hydraulic motor becomes with piston head.
33. device according to claim 29, wherein, regardless of fluid flow direction, the sense of rotation of described oil hydraulic motor remains unchanged.
34. device according to claim 29, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
35. device according to claim 34, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
36. device according to claim 34, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
37. device according to claim 34, wherein, described at least one hydrovalve is electronic control valve.
38. device according to claim 29, described device combines with the single-cylinder type damper.
39. device according to claim 29, described device combines with the double barreled damper.
40. device according to claim 29, described device combines with three cartridge type dampers.
41. device according to claim 29 also comprises generator and controller, wherein, is connected to described controller function described generator.
42. described device according to claim 41, wherein, described controller is at least in part by described generator powered.
43. described device according to claim 41, wherein, described controller outputs to external loading with energy from described generator.
44. described device according to claim 41, wherein, described controller is suitable for controlling Fluid Flow in A by described oil hydraulic motor by the electrology characteristic of controlling described generator.
45. described device according to claim 44, wherein, described electrology characteristic is the electromotive force of described generator.
46. described device according to claim 44, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
47. described device according to claim 41, wherein, described generator is controlled so as to and is driven as motor, and described oil hydraulic motor is driven as oil hydraulic pump.
48. device according to claim 29, wherein, described oil hydraulic motor is suitable for providing damping force.
49. an energy recycle device comprises:
Gerotor;
Generator, described generator functionally is connected to described gerotor; And
One or more valve, described one or more valve is communicated with the via fluid that gets around described gerotor, wherein, at least one valve in described one or more valve is suitable for optionally opening to limit the pressure that is applied to described gerotor by described path by the permission Fluid Flow in A.
50. described energy recycle device according to claim 49, wherein, described valve is the one-way valve that is suitable for controlling the damping characteristic of described energy recycle device.
51. described energy recycle device according to claim 49, wherein, described valve is the escape valve that is suitable for limiting the pressure maximum that is applied to described gerotor.
52. described energy recycle device according to claim 49, wherein, it is whole that described gerotor becomes with described piston head.
53. 2 described energy recycle devices according to claim 5, wherein, it is whole that described generator becomes with described piston head.
54. 2 described energy recycle devices according to claim 5 comprise that also piston rod and the electric wire of hollow, the piston rod of described hollow comprise passage and functionally be attached to described piston head, described electric wire passes described channel routing and is electrically connected to described generator.
55. described energy recycle device according to claim 49, wherein, described gerotor and described generator are incorporated on the sidepiece of damper body.
56. described energy recycle device according to claim 49, wherein, described gerotor and described generator are incorporated in the base portion of damper body.
57. described energy recycle device according to claim 49, wherein, described gerotor and described generator are basically concentric.
58. described energy recycle device according to claim 49, wherein, described gerotor and described generator are basically coplanar.
59. described energy recycle device according to claim 49, wherein, described gerotor and described generator are basically coplanar and basically concentric.
60. described energy recycle device also is included as the bearing that described gerotor and described generator share according to claim 49.
61. described energy recycle device according to claim 49, described gerotor further comprises the outside inner gear oil pump element that functionally is connected to described generator.
62. described energy recycle device also comprises water-hammer arrester according to claim 49, described water-hammer arrester functionally is connected to described generator with described gerotor.
63. 2 described energy recycle devices according to claim 6, wherein, described water-hammer arrester comprises the open type spring pin.
64. described energy recycle device according to claim 49, wherein, regardless of fluid flow direction, the sense of rotation of described gerotor remains unchanged.
65. described energy recycle device according to claim 49, wherein, fluid is getting around described gerotor when first direction flows, and is activating described gerotor when second direction flows.
66. described energy recycle device according to claim 49 wherein, activates described gerotor and described generator along the Fluid Flow in A of first direction, and activates described gerotor and described generator along the Fluid Flow in A of second direction.
67. described energy recycle device according to claim 49, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
68. 7 described energy recycle devices according to claim 6, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
69. 7 described energy recycle devices according to claim 6, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
70. 7 described energy recycle devices according to claim 6, wherein, described at least one hydrovalve is electronic control valve.
71. described energy recycle device according to claim 49, wherein, described energy recycle device combines with the single-cylinder type damper.
72. described energy recycle device according to claim 49, described energy recycle device combines with the double barreled damper.
73. described energy recycle device according to claim 49, described energy recycle device combines with three cartridge type dampers.
74. described energy recycle device according to claim 49, described energy recycle device combines with rotary type damper.
75. described energy recycle device also comprises the controller that functionally is connected to described generator according to claim 49.
76. want 75 described energy recycle devices according to right, wherein, described controller is at least in part by described generator powered.
77. 5 described energy recycle devices according to claim 7, wherein, described controller outputs to external loading with energy from described generator.
78. 5 described energy recycle devices according to claim 7, wherein, described controller is suitable for controlling Fluid Flow in A by described gerotor by the electrology characteristic of controlling described generator.
79. 8 described energy recycle devices according to claim 7, wherein, described electrology characteristic is the electromotive force of described generator.
80. 8 described energy recycle devices according to claim 7, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
81. described energy recycle device according to claim 49, wherein, described generator is controlled so as to and is driven as motor, and described gerotor is driven as oil hydraulic pump.
82. described energy recycle device according to claim 49, wherein, at least one in described gerotor, described generator and described one or more valve is suitable for providing damping force.
83. an energy recycle device comprises:
Gerotor, described gerotor comprises inner member and outer member; And
Generator, described generator are connected to the generator amature of described outer member with comprising direct control; And
At least one bearing, described at least one bearing supports in described rotor and the described outer member at least one.
84. 3 described energy recycle devices according to claim 8, wherein, described outer member comprises periphery, and wherein, described rotor directly is connected to the described periphery of described outer member.
85. 3 described energy recycle devices according to claim 8, wherein, it is whole that described gerotor becomes with described piston head.
86. it is whole that 5 described energy recycle devices according to claim 8, wherein said generator become with described piston head.
87. 5 described energy recycle devices according to claim 8 comprise that also piston rod and the electric wire of hollow, the piston rod of described hollow comprise passage and functionally be attached to described piston head, described electric wire passes described channel routing and is electrically connected to described generator.
88. 3 described energy recycle devices also comprise water-hammer arrester according to claim 8, described water-hammer arrester is connected to described generator amature with described gerotor.
89. 8 described energy recycle devices according to claim 8, wherein, described water-hammer arrester comprises the open type spring pin.
90. 3 described energy recycle devices according to claim 8, wherein, regardless of the flow direction of fluid, the sense of rotation of described gerotor remains unchanged.
91. 3 described energy recycle devices according to claim 8, wherein, fluid is getting around described gerotor when first direction flows, and is activating described gerotor when second direction flows.
92. 3 described energy recycle devices according to claim 8 wherein, activate described gerotor and described generator along the Fluid Flow in A of first direction, and activate described gerotor and described generator along the Fluid Flow in A of second direction.
93. 3 described energy recycle devices according to claim 8, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
94. 3 described devices according to claim 9, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
95. 3 described devices according to claim 9, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
96. 3 described devices according to claim 9, wherein, described at least one hydrovalve is electronic control valve.
97. 3 described energy recycle devices according to claim 8, described energy recycle device combines with the single-cylinder type damper.
98. 3 described energy recycle devices according to claim 8, described energy recycle device combines with the double barreled damper.
99. 3 described energy recycle devices according to claim 8, described energy recycle device combines with three cartridge type dampers.
100. 3 described energy recycle devices according to claim 8, described energy recycle device combines with rotary type damper.
101. 3 described energy recycle devices also comprise the controller that functionally is connected to described generator according to claim 8.
102. 1 described energy recycle device according to claim 10, wherein, described controller is at least in part by described generator powered.
103. 1 described energy recycle device according to claim 10, wherein, described controller outputs to external loading with energy from described generator.
104. 1 described energy recycle device according to claim 10, wherein, described controller is suitable for controlling Fluid Flow in A by described gerotor by the electrology characteristic of controlling described generator.
105. 4 described energy recycle devices according to claim 10, wherein, described electrology characteristic is the electromotive force of described generator.
106. 4 described energy recycle devices according to claim 10, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
107. 3 described energy recycle devices according to claim 8, wherein, described generator is controlled so as to and is driven as motor, and described gerotor is driven as oil hydraulic pump.
108. described energy recycle device according to claim 49, wherein, at least one in described gerotor and the described generator is suitable for providing damping force.
109. an energy recycle device comprises:
Oil hydraulic motor, described oil hydraulic motor comprise the first port and the second port;
Generator, described generator functionally is connected to described oil hydraulic motor;
The first volume, described the first volume is communicated with described the first port fluid, and wherein, when to the pressurized with fluid in described the first volume, fluid flows to described the first port from described the first volume;
The second volume, described the second volume and described the first volume optionally fluid are communicated with, wherein, when to the pressurized with fluid in described the second volume, fluid flows to described the first volume and from described the first volume from described the second volume and flows to described the first port;
110. 9 described energy recycle devices according to claim 10 also comprise and described the second volume low pressure volume of being communicated with of fluid optionally.
111. 0 described energy recycle device also comprises one-way valve according to claim 11, wherein, when giving described the second volume decompression, fluid flows to described the second volume from described low pressure volume.
112. 0 described energy recycle device according to claim 11, wherein, described low pressure volume further comprises compressible medium.
113. 0 described energy recycle device according to claim 11 comprises the controlled valve that optionally allows described low pressure chamber to be communicated with fluid between described the second volume.
114. 3 described energy recycle devices according to claim 11, wherein, described controlled valve is electronic control valve.
115. 9 described energy recycle devices according to claim 10 comprise the controlled valve that optionally allows described the first port to be communicated with fluid between described the second volume.
116. 5 described energy recycle devices according to claim 11, wherein, described controlled valve is electronic control valve.
117. 9 described energy recycle devices according to claim 10, the one-way valve that the selectivity fluid that also comprising provides from described the second volume to described the first volume is communicated with.
118. 9 described energy recycle devices according to claim 10, also comprise the piston that is arranged in the chamber that limits described the first volume and described the second volume, wherein, described piston is suitable between primary importance and the second place mobile, thereby described the first volume and described the second volume are changed.
119. 8 described energy recycle devices according to claim 11, wherein, described piston further comprises directional check valve, and described directional check valve provides the selectivity fluid from described the second volume to described the first volume to be communicated with.
120. 9 described energy recycle devices according to claim 10, wherein, described oil hydraulic motor and described generator are basically concentric.
121. 9 described energy recycle devices according to claim 10, wherein, described oil hydraulic motor and described generator are basically coplanar.
122. 9 described energy recycle devices according to claim 10, wherein, described oil hydraulic motor and described generator are basically coplanar and basically concentric.
123. 9 described energy recycle devices also are included as the bearing that described oil hydraulic motor and described generator share according to claim 10.
124. 9 described energy recycle devices according to claim 10, wherein, described oil hydraulic motor is gerotor.
125. 4 described energy recycle devices according to claim 12, wherein, described gerotor further comprises the outside inner gear oil pump element that functionally is connected to described generator.
126. 9 described energy recycle devices also comprise water-hammer arrester according to claim 10, described water-hammer arrester functionally is connected to described generator with described oil hydraulic motor.
127. 6 described energy recycle devices according to claim 12, wherein, described water-hammer arrester comprises the open type spring pin.
128. 9 described energy recycle devices according to claim 10, wherein, described the first volume and described the second volume are limited by the chamber in the three cartridge type dampers.
129. 8 described energy recycle devices according to claim 12, wherein, described oil hydraulic motor is contained in the described three cartridge type dampers.
130. 8 described energy recycle devices according to claim 12, wherein, described hydraulic motor arrangement is on the base portion of described three cartridge type dampers or on the sidepiece.
131. 9 described energy recycle devices also comprise the controller that functionally is connected to described generator according to claim 10.
132. 1 described energy recycle device according to claim 13, wherein, described controller is at least in part by described generator powered.
133. 1 described energy recycle device according to claim 13, wherein, described controller is suitable for controlling Fluid Flow in A by described oil hydraulic motor by the electrology characteristic of controlling described generator.
134. 3 described energy recycle devices according to claim 13, wherein, described electrology characteristic is the electromotive force of described generator.
135. 3 described energy recycle devices according to claim 13, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
136. 9 described energy recycle devices according to claim 10, wherein, described generator is controlled so as to and is driven as motor, and described oil hydraulic motor is driven as oil hydraulic pump.
137. 9 described energy recycle devices according to claim 10, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
138. 7 described energy recycle devices according to claim 13, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
139. 7 described energy recycle devices according to claim 13, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
140. 7 described energy recycle devices according to claim 13, wherein, at least one hydrovalve is electronic control valve.
141. 7 described energy recycle devices according to claim 13, wherein, at least one in described oil hydraulic motor, described generator and the described controller is suitable for providing damping force.
142. an energy recycle device comprises:
Rotary type damper, described rotary type damper have the first side and the second side, thereby and be suitable for being arranged in the housing of fluid filling and be immersed in the described fluid;
Oil hydraulic motor, described oil hydraulic motor is connected with described rotary type damper, wherein, described oil hydraulic motor has the first port and the second port, described the first port and the fluid communication that is adjacent to described first side of described rotary type damper, described the second port and the fluid communication that is adjacent to described second side of described rotator type damper; And
Generator, described generator functionally is connected to described oil hydraulic motor.
143. 2 described energy recycle devices according to claim 14, wherein, described oil hydraulic motor is gerotor.
144. 3 described energy recycle devices according to claim 14, wherein, described gerotor further comprises the outside inner gear oil pump element that functionally is connected to described generator.
145. 2 described energy recycle devices according to claim 14, wherein, described oil hydraulic motor becomes whole with described generator with described rotary type damper.
146. 2 described energy recycle devices according to claim 14, wherein, described oil hydraulic motor and described generator are basically concentric.
147. 2 described energy recycle devices according to claim 14, wherein, described oil hydraulic motor and described generator are basically coplanar.
148. 2 described energy recycle devices according to claim 14, wherein, described oil hydraulic motor and described generator are basically coplanar and basically concentric.
149. 2 described energy recycle devices also are included as the bearing that described oil hydraulic motor and described generator share according to claim 14.
150. 2 described energy recycle devices also comprise water-hammer arrester according to claim 14, described water-hammer arrester functionally is connected to described generator with described oil hydraulic motor.
151. 0 described energy recycle device according to claim 15, wherein, described water-hammer arrester comprises the open type spring pin.
152. 2 described energy recycle devices according to claim 14, wherein, described rotary type damper is suitable between primary importance and the second place mobile, no matter described rotary type damper is that the sense of rotation of described oil hydraulic motor remains unchanged mobile between described primary importance and the described second place or mobile between the described second place and described primary importance.
153. 2 described energy recycle devices according to claim 14, wherein, at least some fluids are getting around described oil hydraulic motor and activating described oil hydraulic motor when second direction flow when first direction flows.
154. 2 described energy recycle devices according to claim 14, wherein, at least some fluids are allowed to flow through at least one hydrovalve in parallel with described oil hydraulic motor or that connect.
155. 4 described devices according to claim 15, wherein, described at least one hydrovalve is suitable at predetermined pressure operation.
156. 4 described devices according to claim 15, wherein, described at least one hydrovalve provides unidirectional Fluid Flow in A.
157. 4 described devices according to claim 15, wherein, described at least one hydrovalve is electronic control valve.
158. 2 described energy recycle devices according to claim 14 wherein, activate described oil hydraulic motor and described generator along the Fluid Flow in A of first direction, and activate described oil hydraulic motor and described generator along the Fluid Flow in A of second direction.
159. 2 described energy recycle devices also comprise the controller that functionally is connected to described generator according to claim 14.
160. 9 described energy recycle devices according to claim 15, wherein, described controller is at least in part by described generator powered.
161. 9 described energy recycle devices according to claim 15, wherein, described controller outputs to external loading with energy from described generator.
162. 9 described energy recycle devices according to claim 15, wherein, described controller is suitable for controlling Fluid Flow in A by described oil hydraulic motor by the electrology characteristic of controlling described generator.
163. 2 described energy recycle devices according to claim 16, wherein, described electrology characteristic is the electromotive force of described generator.
164. 2 described energy recycle devices according to claim 16, wherein, described electrology characteristic is the impedance that is applied to the terminal of described generator.
165. 2 described energy recycle devices according to claim 14, wherein, described generator is controlled so as to and is driven as motor, and described oil hydraulic motor is driven as oil hydraulic pump.
166. 2 described energy recycle devices according to claim 14, wherein, at least one in described rotary type damper, described oil hydraulic motor and the described generator is suitable for providing damping force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510856537.2A CN105386951B (en) | 2010-06-16 | 2011-06-16 | Integrated energy generating damper |
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| Application Number | Priority Date | Filing Date | Title |
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| US35518610P | 2010-06-16 | 2010-06-16 | |
| US61/355,186 | 2010-06-16 | ||
| US201161467161P | 2011-03-24 | 2011-03-24 | |
| US61/467,161 | 2011-03-24 | ||
| PCT/US2011/040654 WO2011159874A2 (en) | 2010-06-16 | 2011-06-16 | Integrated energy generating damper |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510856537.2A Division CN105386951B (en) | 2010-06-16 | 2011-06-16 | Integrated energy generating damper |
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| CN103080544A true CN103080544A (en) | 2013-05-01 |
| CN103080544B CN103080544B (en) | 2015-11-25 |
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| CN201510856537.2A Active CN105386951B (en) | 2010-06-16 | 2011-06-16 | Integrated energy generating damper |
| CN201180038655.2A Active CN103080544B (en) | 2010-06-16 | 2011-06-16 | Integrated energy produces damper |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510856537.2A Active CN105386951B (en) | 2010-06-16 | 2011-06-16 | Integrated energy generating damper |
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| Country | Link |
|---|---|
| US (7) | US9035477B2 (en) |
| EP (3) | EP4289640A3 (en) |
| JP (6) | JP5723445B2 (en) |
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| WO (1) | WO2011159874A2 (en) |
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